US20090252616A1 - Variable Rate Pumping System - Google Patents
Variable Rate Pumping System Download PDFInfo
- Publication number
- US20090252616A1 US20090252616A1 US12/484,961 US48496109A US2009252616A1 US 20090252616 A1 US20090252616 A1 US 20090252616A1 US 48496109 A US48496109 A US 48496109A US 2009252616 A1 US2009252616 A1 US 2009252616A1
- Authority
- US
- United States
- Prior art keywords
- pump
- fluid
- flow rate
- motor
- pressure
- 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
Images
Classifications
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
- F04B49/065—Control using electricity and making use of computers
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1201—Rotational speed of the axis
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1202—Torque on the axis
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1203—Power on the axis
-
- 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
- F04B2203/00—Motor parameters
- F04B2203/02—Motor parameters of rotating electric motors
- F04B2203/0209—Rotational speed
-
- 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
- F04B2205/00—Fluid parameters
- F04B2205/05—Pressure after the pump outlet
-
- 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
- F04B2205/00—Fluid parameters
- F04B2205/09—Flow through the pump
Definitions
- the present invention relates generally to methods and apparatus for supplying pressurized fluids. More particularly, the present invention relates to methods and apparatus for pumping fluids into a wellbore at a wide range of pressures and flow rates.
- fluids may be pumped into a well in conjunction with activities including fracturing, completion, stimulation, remediation, cementing, workover, and testing operations.
- activities including fracturing, completion, stimulation, remediation, cementing, workover, and testing operations.
- a variety of fluids used in these operations include fracturing fluids, gels, drilling mud, barite, cement, slurries, acids, and liquid CO 2 .
- the fluid may be required to be pumped into the well at any point within a wide range of pressures and flow rates.
- Pumping units often utilize a power source, such as a diesel or electric motor, to drive one or more pumps.
- a power source such as a diesel or electric motor
- Many pumping units utilize a multispeed transmission connected between the power source and the pumps.
- the transmission operates to expand the speed and torque range produced by the power source by providing a set number of gears that transfer the motion produced by the power source to the pump.
- This operating envelope 10 can be illustrated as a relationship between pressure and flow rate as is shown in FIG. 1 .
- Line 15 defines the peak hydraulic horsepower at which the pump can operate and line 16 defines the peak torque output.
- the transmission comprises a limited set of gear ratios 17 , the operating envelope 10 of the pump has discrete points 20 at which the pump can operate at peak hydraulic horsepower. These discrete points 20 , in effect, create gaps 25 where the pump cannot operate with a given gearing.
- gaps 25 can be reduced by increasing the numbers of gear ratios within a transmission, as the number of gear ratios increases so does the complexity and weight of the transmission. Therefore, there are often practical limits on the number of gear ratios at which a transmission can operate. Thus, there remains a need to develop methods and apparatus for pumping fluids into a wellbore at wide range of pressures and flow rates, which overcome some of the foregoing difficulties while providing more advantageous overall results.
- a wellbore pumping system comprising a motor, wherein the motor has an operating speed, a pump coupled to the motor, wherein the pump has a volumetric displacement, a fluid end coupled to the pump, wherein the fluid end is operable to draw fluid from an input and provide fluid to an output that is in fluid communication with a wellbore, and a control system operable to regulate the motor and the pump in order to provide fluid to the output at a selected pressure and flow rate within a continuous range of pressures and flow rates between the peak horsepower output and peak torque output of the motor.
- a method for operating a wellbore pumping system comprising operating a pumping system to provide fluid to a wellbore at a selected pressure and flow rate operating conditions within a continuous range of pressures and flow rates between the peak horsepower and peak torque of the pumping system, monitoring the pressure and flow rate of the fluid provided by the pumping system, and controlling the pumping system to provide non-discrete variations in the pressure and flow rate of the fluid provided to the wellbore.
- a pumping system comprising a motor having an operating speed, a variable displacement pump coupled to the motor, wherein the positive displacement pump has an operating speed that is related to the operating speed of the motor by a fixed ratio, a fluid end coupled to the pump, wherein the fluid end is operable to draw fluid from an inlet and provide fluid to an outlet that is in fluid communication with a wellbore, and a control system operable to regulate the operating speed of the motor and the displacement of the pump so as to control the pressure and flow rate of the fluid provided to the outlet.
- a method of operating a wellbore servicing pump comprising controlling the operating parameters of the pump to provide a fluid output at any combination of pressure and flow rate within a range defined by the peak hydraulic horsepower, the peak torque, the maximum pressure, and the maximum flow rate of the pump, monitoring pressure and flow rate of the fluid output, adjusting at least one of the operating parameters of the pump to provide a desired pressure and flow rate of the fluid output.
- the present invention comprises a combination of features and advantages that enable it to overcome various problems of prior devices.
- the various characteristics described above, as well as other features, will be readily apparent to those skilled in the art upon reading the following detailed description of the invention, and by referring to the accompanying drawings.
- FIG. 1 is a graphical representation of the output characteristics of a prior art pumping system employing a multispeed transmission.
- FIG. 2 is a schematic illustration of a pumping system constructed in accordance with embodiments of the invention.
- FIG. 3 is a schematic illustration of a control system for a pumping system constructed in accordance with embodiments of the invention.
- FIG. 4 is a graphical representation of the output characteristics of a pumping system constructed in accordance with embodiments of the invention.
- FIG. 5 is an isometric view of one embodiment of a pumping system constructed in accordance with embodiments of the invention.
- FIG. 6 is an isometric view of the displacement controller of FIG. 5 .
- FIG. 7 is a cross-sectional view of a coupler of the displacement controller of FIG. 5 .
- pump system 200 comprises motor 210 , pump 220 , fluid end assembly 230 , control system 240 , and displacement control 250 .
- Motor 210 is coupled to pump 220 and provides power to the pump.
- Pump 220 works through fluid end assembly 230 to pull fluid from inlet 260 to outlet 270 .
- Control system 240 monitors the flow conditions (e.g. flow rate and pressure) at outlet 270 and regulates motor 210 and pump 220 , through displacement control 250 , to maintain a desired flow rate and pressure.
- Pump 220 is linked to motor 210 without a transmission, such that their speeds are related by a fixed ratio.
- the speed of pump 220 may be directly regulated by controlling the speed of motor 210 .
- Displacement control 250 regulates the displacement (or volume of fluid) that pump 220 will move with each revolution or reciprocation.
- displacement control 250 may act to vary the displacement of pump 220 by changing the volume of fluid pumped per stroke of a pump cylinder.
- Control system 240 comprises servo valve 310 , positioner 320 , input/output (I/O) device 330 , processor 340 , and power supply 350 .
- Servo valve 310 and positioner 320 may be integrated into displacement control 250 of FIG. 2 .
- Servo valve 310 may be an electric, hydraulic, or electro-hydraulic valve providing control of positioner 320 .
- Positioner 320 may be an electric or hydraulic actuator operable to interface with a displacement determining arrangement within pump 220 .
- I/O device 330 monitors the position of positioner 320 via line 373 and regulates the operation of servo valve 310 via line 375 in order to control the position of the positioner.
- I/O device 330 controls the position of positioner 320 in response to flow data 360 received from outlet 270 (see FIG. 2 ).
- Processor 340 powered by power supply 350 , controls the activity of I/O devices 330 in response to operator inputs or from a pre-programmed procedure.
- I/O devices 330 may comprise two separate devices, one for position input, and one for servo valve output, such as SDS CAN analog input and output modules.
- Processor 340 may be an ACE industrial PC with a board that connects the PC to the I/O devices 330 .
- processor 340 receives an instruction to provide a fluid output having a desired flow rate and pressure from fluid end assembly 230 .
- Processor 340 determines a motor speed and pump displacement that will provide the desired fluid output by referencing a predetermined reference table or by calculating the appropriate values.
- Processor 340 transmits the corresponding predetermined motor speed and pump displacement drive signals for the desired flow conditions to I/O devices 330 .
- I/O devices 330 send instructions to displacement control 250 via line 375 and motor 210 via line 370 .
- Displacement control 250 establishes the displacement for pump 220 by setting positioner 320 using servo valve 310 .
- Speed control commands 370 are issued to motor 210 from I/O device 330 of control system 240 .
- I/O device 330 receives flow data 360 from outlet 270 and adjusts motor 210 and displacement control 250 to maintain the desired flow characteristics.
- the motor speed and displacement can be optimized for horsepower, torque, fuel efficiency, or a combination of those factors. For example, if maximum horsepower is selected, the engine speed (and thus pump speed) and pump displacement would be chosen to give the best rate for maximum engine horsepower to be developed. Thus, maximum horsepower would be transferred to the pump and to the fluid being pumped. Similar choices could be made for optimal efficiency, or for optimal torque. In each case, the engine speed and displacement would be chosen to allow for the optimum parameter value to be developed by the engine and transferred to the pump with much lower loss than with a transmission.
- the engine speed and the pump stroke (displacement) would be chosen to allow the engine to operate at optimum efficiency, saving fuel and reducing emissions.
- the efficiency would be greater not only because of operating the engine at its optimal speed for the load but would also be greater than with a transmission because losses from the transmission, which lower efficiency, would be avoided.
- a continuous feedback control loop also allows for adjusting to changing fluid conditions, including compressibility and inlet flow rate, and provides a quick-to-neutral capability.
- the quick-to-neutral capability offers a significant advantage should a pumping shutdown be needed.
- a relief valve When activated, a relief valve would quickly release the hydraulic pressure that was holding the current pump displacement and fluid back pressure would rapidly stroke the positioner back to the zero rate pumping position. This could be done much more quickly than stopping the engine or pump from rotating, because to stop them, their inertia must be overcome.
- This ability could be further enhanced by incorporating a spring in the displacement actuator so that when pumping against low pressure, the spring would assist in more rapidly returning the pump to the zero pumping rate position.
- an operating envelope 400 for pump system 200 can be illustrated as a relationship between pressure and flow rate. Because there are no distinct gear ratios, as are shown in FIG. 1 , operating envelope 400 includes all pressure and flow rate combinations within the operational limits of peak hydraulic horsepower 410 , peak torque output 415 , maximum operating pressure 420 , maximum flow rate 430 , and minimum flow rate 440 . Therefore, pump system 200 can operate within a continuous range of pressure and flowrate combinations between peak hydraulic horsepower 410 and peak torque output 415 . When compared to the prior art multispeed transmission operating envelope of FIG. 1 , the operating envelope of FIG. 4 has no gaps between peak hydraulic horsepower 410 and peak torque output 415 where there are pressure and flow rate combinations where the system cannot operate.
- Eliminating the multispeed transmission also eliminates a complex piece of machinery, reducing capital and maintenance costs as well as reducing the weight of the overall system.
- Many pumping systems are portable systems that are mounted on skids, trailers, or chassis, so weight and size of components is an important issue. For example, to be easily transported by road, the size of a portable component of a system is limited to a width of approximately eight feet and a height of approximately thirteen feet. With the weight of the multispeed transmission eliminated, a higher horsepower or capacity system could be used in applications that were previously limited by the weight and/or size of the components.
- Embodiments of pumping system 200 may utilize any combination of motors, variable displacement pumps, and fluid end assemblies as may be desired.
- an electric or diesel motor may be used to provide power to the pump.
- the pump may be any variable displacement pump providing easily adjusted variable displacement and capable of the horsepower and pressure requirements needed for the desired application.
- pumps may be used having mechanisms as described in U.S. Pat. No. 6,742,441, entitled “Continuously Variable Displacement Pump with Predefined Unswept Volume,” or U.S. Pat. No. 6,976,831 filed Jun. 25, 2003, entitled “Transmissionless Variable Output Pumping Unit,” or U.S. Pat. No. 7,409,901 filed Oct. 27, 2004, entitled “Variable Stroke Assembly,” all of which are incorporated herein by reference in their entirety for all purposes.
- a pump system 500 including displacement controller 510 , speed reducer 520 , variable displacement pump 530 , and fluid end 540 .
- Pump system 500 is powered by an electric motor or diesel engine (not shown) through drive line connection 550 .
- Variable displacement pump 530 comprises a “Sanderson mechanism” as is shown and described in U.S. Pat. No. 6,019,073, entitled “Double Ended Piston Engine,” and U.S. Pat. No. 6,397,794, entitled “Piston Engine Assembly,” and U.S. Pat. No. 6,446,587, entitled “Piston Engine Assembly,” all of which are incorporated herein by reference in their entirety for all purposes.
- Variable displacement pump 530 includes a rotating shaft, the position of which can be linearly adjusted to control the displacement of the pump.
- the shaft is rotated by the motor turning drive line connection 550 , which is coupled to the shaft through speed reducer 520 .
- Speed reducer 520 transfers rotation from drive line connection 550 to the shaft at a fixed ratio as established by one or more gears disposed within the speed reducer.
- the rotational rate of pump 530 is directly proportional to the rotational rate at which the motor is operated.
- the displacement of pump 530 is controlled by axially displacing the rotating shaft that is coupled to the motor.
- the displacement of the rotating shaft can be controlled by a variety of devices including hydraulic cylinders, jack-screws, ball-screws, pneumatic cylinders, and electric actuators. These devices preferably provide adjustment of the rotating shaft in both directions along its axis. Referring back to FIG. 3 , these control devices act as positioner 320 that is controlled by servo 310 .
- displacement controller 510 controls the linear displacement of the rotating shaft 602 .
- Displacement controller 510 includes coupler 604 that interfaces between shaft 602 and hydraulic piston 606 .
- Hydraulic piston 606 is connected to the power end of pump 530 by tie rods 608 .
- Coupler 604 supports rotational movement of shaft 602 and allows hydraulic piston 606 to apply an axial force to move shaft 602 and thus adjust the stroke of pump 530 .
- coupler 604 includes housing 610 , bearings 612 , rotating retainer 614 , and connecting screw 616 .
- Housing 610 is mounted to pump 530 and includes flange 618 .
- the extending shaft of hydraulic piston 606 see FIG. 6 , engages flange 618 to apply linear force to housing 610 .
- Shaft 602 see FIG. 6 , is attached to screw 616 , which is connected to rotating retainer 614 and allowed to rotate relative to housing 610 by bearing 612 . Therefore, shaft 602 can freely rotate about its longitudinal axis as it is moved along that axis by piston 606 .
- the stroke of those pistons is controlled by displacement controller 510 .
- the output pressure and flow rate can be regulated.
- Fluid end 540 is coupled to the pistons of pump 530 such that fluid is drawn in through suction inlet 560 and expelled through fluid outlet 570 .
- Fluid end 540 may comprise check valve assemblies 580 that interface with the pistons of pump 530 , where each check valve 580 is in fluid communication with both inlet 560 and outlet 570 .
- the check valve assemblies 580 allow fluid to be drawn only from the low pressure inlet 560 and high pressure fluid output only through outlet 570 .
- variable displacement pumping system By eliminating the need for a heavy-duty, multi-speed transmission, the variable displacement pumping system provides a smaller package for a given pump rating.
- the table below lists various examples of pumping systems operating at 275 revolutions per minute.
- variable displacement pumping system provides a more complete operating envelope as compared to conventional transmission systems.
Abstract
A pumping system comprising a motor, wherein the motor has an operating speed, a pump coupled to the motor, wherein the pump has a volumetric displacement, a fluid end coupled to the pump, wherein the fluid end is operable to draw fluid from an input and provide fluid to an output, and a control system operable to regulate the motor and the pump in order to provide fluid to the output at a selected pressure and flow rate within a continuous range of pressures and flow rates between the peak horsepower output and peak torque output of the motor.
Description
- The present application is a divisional of U.S. patent application Ser. No. 10/974,437, filed Oct. 27, 2004, and entitled “Variable Rate Pumping System,” which is incorporated herein by reference as if reproduced in its entirety.
- Not Applicable.
- The present invention relates generally to methods and apparatus for supplying pressurized fluids. More particularly, the present invention relates to methods and apparatus for pumping fluids into a wellbore at a wide range of pressures and flow rates.
- The construction and servicing of subterranean wells often involves pumping fluids into the well for a variety of reasons. For example, fluids may be pumped into a well in conjunction with activities including fracturing, completion, stimulation, remediation, cementing, workover, and testing operations. A variety of fluids used in these operations include fracturing fluids, gels, drilling mud, barite, cement, slurries, acids, and liquid CO2. In each of these different applications, the fluid may be required to be pumped into the well at any point within a wide range of pressures and flow rates.
- Pumping units often utilize a power source, such as a diesel or electric motor, to drive one or more pumps. Many pumping units utilize a multispeed transmission connected between the power source and the pumps. The transmission operates to expand the speed and torque range produced by the power source by providing a set number of gears that transfer the motion produced by the power source to the pump.
- Most multispeed transmissions provide a broad operating envelope of speed and torque within which a pump can operate. This
operating envelope 10 can be illustrated as a relationship between pressure and flow rate as is shown inFIG. 1 .Line 15 defines the peak hydraulic horsepower at which the pump can operate andline 16 defines the peak torque output. Because the transmission comprises a limited set ofgear ratios 17, theoperating envelope 10 of the pump hasdiscrete points 20 at which the pump can operate at peak hydraulic horsepower. Thesediscrete points 20, in effect, creategaps 25 where the pump cannot operate with a given gearing. - Although
gaps 25 can be reduced by increasing the numbers of gear ratios within a transmission, as the number of gear ratios increases so does the complexity and weight of the transmission. Therefore, there are often practical limits on the number of gear ratios at which a transmission can operate. Thus, there remains a need to develop methods and apparatus for pumping fluids into a wellbore at wide range of pressures and flow rates, which overcome some of the foregoing difficulties while providing more advantageous overall results. - Disclosed herein is a wellbore pumping system comprising a motor, wherein the motor has an operating speed, a pump coupled to the motor, wherein the pump has a volumetric displacement, a fluid end coupled to the pump, wherein the fluid end is operable to draw fluid from an input and provide fluid to an output that is in fluid communication with a wellbore, and a control system operable to regulate the motor and the pump in order to provide fluid to the output at a selected pressure and flow rate within a continuous range of pressures and flow rates between the peak horsepower output and peak torque output of the motor.
- Further disclosed herein is a method for operating a wellbore pumping system, the method comprising operating a pumping system to provide fluid to a wellbore at a selected pressure and flow rate operating conditions within a continuous range of pressures and flow rates between the peak horsepower and peak torque of the pumping system, monitoring the pressure and flow rate of the fluid provided by the pumping system, and controlling the pumping system to provide non-discrete variations in the pressure and flow rate of the fluid provided to the wellbore. Further disclosed herein is a pumping system comprising a motor having an operating speed, a variable displacement pump coupled to the motor, wherein the positive displacement pump has an operating speed that is related to the operating speed of the motor by a fixed ratio, a fluid end coupled to the pump, wherein the fluid end is operable to draw fluid from an inlet and provide fluid to an outlet that is in fluid communication with a wellbore, and a control system operable to regulate the operating speed of the motor and the displacement of the pump so as to control the pressure and flow rate of the fluid provided to the outlet.
- Further disclosed herein is a method of operating a wellbore servicing pump comprising controlling the operating parameters of the pump to provide a fluid output at any combination of pressure and flow rate within a range defined by the peak hydraulic horsepower, the peak torque, the maximum pressure, and the maximum flow rate of the pump, monitoring pressure and flow rate of the fluid output, adjusting at least one of the operating parameters of the pump to provide a desired pressure and flow rate of the fluid output.
- Thus, the present invention comprises a combination of features and advantages that enable it to overcome various problems of prior devices. The various characteristics described above, as well as other features, will be readily apparent to those skilled in the art upon reading the following detailed description of the invention, and by referring to the accompanying drawings.
- For a more detailed description of the present invention, reference will now be made to the accompanying drawings, wherein:
-
FIG. 1 is a graphical representation of the output characteristics of a prior art pumping system employing a multispeed transmission. -
FIG. 2 is a schematic illustration of a pumping system constructed in accordance with embodiments of the invention. -
FIG. 3 is a schematic illustration of a control system for a pumping system constructed in accordance with embodiments of the invention. -
FIG. 4 is a graphical representation of the output characteristics of a pumping system constructed in accordance with embodiments of the invention. -
FIG. 5 is an isometric view of one embodiment of a pumping system constructed in accordance with embodiments of the invention. -
FIG. 6 is an isometric view of the displacement controller ofFIG. 5 . -
FIG. 7 is a cross-sectional view of a coupler of the displacement controller ofFIG. 5 . - Referring now to an embodiment shown in
FIG. 2 ,pump system 200 comprisesmotor 210,pump 220,fluid end assembly 230,control system 240, anddisplacement control 250.Motor 210 is coupled topump 220 and provides power to the pump.Pump 220 works throughfluid end assembly 230 to pull fluid frominlet 260 tooutlet 270.Control system 240 monitors the flow conditions (e.g. flow rate and pressure) atoutlet 270 and regulatesmotor 210 andpump 220, throughdisplacement control 250, to maintain a desired flow rate and pressure. -
Pump 220 is linked tomotor 210 without a transmission, such that their speeds are related by a fixed ratio. Thus, the speed ofpump 220 may be directly regulated by controlling the speed ofmotor 210.Displacement control 250 regulates the displacement (or volume of fluid) thatpump 220 will move with each revolution or reciprocation. For example,displacement control 250 may act to vary the displacement ofpump 220 by changing the volume of fluid pumped per stroke of a pump cylinder. - One embodiment of
control system 240 is shown inFIG. 3 .Control system 240 comprisesservo valve 310,positioner 320, input/output (I/O)device 330,processor 340, andpower supply 350.Servo valve 310 andpositioner 320 may be integrated intodisplacement control 250 ofFIG. 2 .Servo valve 310 may be an electric, hydraulic, or electro-hydraulic valve providing control ofpositioner 320.Positioner 320 may be an electric or hydraulic actuator operable to interface with a displacement determining arrangement withinpump 220. I/O device 330 monitors the position ofpositioner 320 vialine 373 and regulates the operation ofservo valve 310 vialine 375 in order to control the position of the positioner. I/O device 330 controls the position ofpositioner 320 in response toflow data 360 received from outlet 270 (seeFIG. 2 ).Processor 340, powered bypower supply 350, controls the activity of I/O devices 330 in response to operator inputs or from a pre-programmed procedure. I/O devices 330 may comprise two separate devices, one for position input, and one for servo valve output, such as SDS CAN analog input and output modules.Processor 340 may be an ACE industrial PC with a board that connects the PC to the I/O devices 330. - Referring now to
FIGS. 2 and 3 , and by way of example,processor 340 receives an instruction to provide a fluid output having a desired flow rate and pressure fromfluid end assembly 230.Processor 340 determines a motor speed and pump displacement that will provide the desired fluid output by referencing a predetermined reference table or by calculating the appropriate values.Processor 340 transmits the corresponding predetermined motor speed and pump displacement drive signals for the desired flow conditions to I/O devices 330. I/O devices 330 send instructions to displacementcontrol 250 vialine 375 andmotor 210 vialine 370.Displacement control 250 establishes the displacement forpump 220 by settingpositioner 320 usingservo valve 310.Speed control commands 370 are issued tomotor 210 from I/O device 330 ofcontrol system 240. - As
pump 220 operates, I/O device 330 receivesflow data 360 fromoutlet 270 and adjustsmotor 210 anddisplacement control 250 to maintain the desired flow characteristics. The motor speed and displacement can be optimized for horsepower, torque, fuel efficiency, or a combination of those factors. For example, if maximum horsepower is selected, the engine speed (and thus pump speed) and pump displacement would be chosen to give the best rate for maximum engine horsepower to be developed. Thus, maximum horsepower would be transferred to the pump and to the fluid being pumped. Similar choices could be made for optimal efficiency, or for optimal torque. In each case, the engine speed and displacement would be chosen to allow for the optimum parameter value to be developed by the engine and transferred to the pump with much lower loss than with a transmission. So, for example, if optimum efficiency is chosen, the engine speed and the pump stroke (displacement) would be chosen to allow the engine to operate at optimum efficiency, saving fuel and reducing emissions. The efficiency would be greater not only because of operating the engine at its optimal speed for the load but would also be greater than with a transmission because losses from the transmission, which lower efficiency, would be avoided. - A continuous feedback control loop also allows for adjusting to changing fluid conditions, including compressibility and inlet flow rate, and provides a quick-to-neutral capability. The quick-to-neutral capability offers a significant advantage should a pumping shutdown be needed. When activated, a relief valve would quickly release the hydraulic pressure that was holding the current pump displacement and fluid back pressure would rapidly stroke the positioner back to the zero rate pumping position. This could be done much more quickly than stopping the engine or pump from rotating, because to stop them, their inertia must be overcome. This ability could be further enhanced by incorporating a spring in the displacement actuator so that when pumping against low pressure, the spring would assist in more rapidly returning the pump to the zero pumping rate position.
- By controlling the speed of
motor 210 and the displacement ofpump 220, any desired pressure and flow rate combination within a given operating envelope can be provided atoutlet 270. Referring now toFIG. 4 , anoperating envelope 400 forpump system 200 can be illustrated as a relationship between pressure and flow rate. Because there are no distinct gear ratios, as are shown inFIG. 1 , operatingenvelope 400 includes all pressure and flow rate combinations within the operational limits of peakhydraulic horsepower 410,peak torque output 415,maximum operating pressure 420,maximum flow rate 430, andminimum flow rate 440. Therefore,pump system 200 can operate within a continuous range of pressure and flowrate combinations between peakhydraulic horsepower 410 andpeak torque output 415. When compared to the prior art multispeed transmission operating envelope ofFIG. 1 , the operating envelope ofFIG. 4 has no gaps between peakhydraulic horsepower 410 andpeak torque output 415 where there are pressure and flow rate combinations where the system cannot operate. - Eliminating the multispeed transmission also eliminates a complex piece of machinery, reducing capital and maintenance costs as well as reducing the weight of the overall system. Many pumping systems are portable systems that are mounted on skids, trailers, or chassis, so weight and size of components is an important issue. For example, to be easily transported by road, the size of a portable component of a system is limited to a width of approximately eight feet and a height of approximately thirteen feet. With the weight of the multispeed transmission eliminated, a higher horsepower or capacity system could be used in applications that were previously limited by the weight and/or size of the components.
- Embodiments of pumping
system 200 may utilize any combination of motors, variable displacement pumps, and fluid end assemblies as may be desired. For example, an electric or diesel motor may be used to provide power to the pump. The pump may be any variable displacement pump providing easily adjusted variable displacement and capable of the horsepower and pressure requirements needed for the desired application. For example, pumps may be used having mechanisms as described in U.S. Pat. No. 6,742,441, entitled “Continuously Variable Displacement Pump with Predefined Unswept Volume,” or U.S. Pat. No. 6,976,831 filed Jun. 25, 2003, entitled “Transmissionless Variable Output Pumping Unit,” or U.S. Pat. No. 7,409,901 filed Oct. 27, 2004, entitled “Variable Stroke Assembly,” all of which are incorporated herein by reference in their entirety for all purposes. - Referring now to
FIG. 5 , one embodiment of apump system 500 is shown includingdisplacement controller 510,speed reducer 520,variable displacement pump 530, andfluid end 540.Pump system 500 is powered by an electric motor or diesel engine (not shown) throughdrive line connection 550.Variable displacement pump 530 comprises a “Sanderson mechanism” as is shown and described in U.S. Pat. No. 6,019,073, entitled “Double Ended Piston Engine,” and U.S. Pat. No. 6,397,794, entitled “Piston Engine Assembly,” and U.S. Pat. No. 6,446,587, entitled “Piston Engine Assembly,” all of which are incorporated herein by reference in their entirety for all purposes. -
Variable displacement pump 530 includes a rotating shaft, the position of which can be linearly adjusted to control the displacement of the pump. The shaft is rotated by the motor turningdrive line connection 550, which is coupled to the shaft throughspeed reducer 520.Speed reducer 520 transfers rotation fromdrive line connection 550 to the shaft at a fixed ratio as established by one or more gears disposed within the speed reducer. Thus, the rotational rate ofpump 530 is directly proportional to the rotational rate at which the motor is operated. - The displacement of
pump 530 is controlled by axially displacing the rotating shaft that is coupled to the motor. The displacement of the rotating shaft can be controlled by a variety of devices including hydraulic cylinders, jack-screws, ball-screws, pneumatic cylinders, and electric actuators. These devices preferably provide adjustment of the rotating shaft in both directions along its axis. Referring back toFIG. 3 , these control devices act aspositioner 320 that is controlled byservo 310. - As shown in
FIG. 6 ,displacement controller 510 controls the linear displacement of therotating shaft 602.Displacement controller 510 includescoupler 604 that interfaces betweenshaft 602 andhydraulic piston 606.Hydraulic piston 606 is connected to the power end ofpump 530 bytie rods 608.Coupler 604 supports rotational movement ofshaft 602 and allowshydraulic piston 606 to apply an axial force to moveshaft 602 and thus adjust the stroke ofpump 530. - Referring now to
FIG. 7 ,coupler 604 includeshousing 610,bearings 612, rotatingretainer 614, and connectingscrew 616.Housing 610 is mounted to pump 530 and includesflange 618. The extending shaft ofhydraulic piston 606, seeFIG. 6 , engagesflange 618 to apply linear force tohousing 610.Shaft 602, seeFIG. 6 , is attached to screw 616, which is connected torotating retainer 614 and allowed to rotate relative tohousing 610 by bearing 612. Therefore,shaft 602 can freely rotate about its longitudinal axis as it is moved along that axis bypiston 606. - Referring back to
FIG. 5 , as the reciprocating speed of the pistons ofpump 530 are driven by the motor throughspeed reducer 520, the stroke of those pistons is controlled bydisplacement controller 510. Thus, by controlling the speed at which the pump reciprocates and the displacement of each stroke of the pump pistons, the output pressure and flow rate can be regulated. -
Fluid end 540 is coupled to the pistons ofpump 530 such that fluid is drawn in throughsuction inlet 560 and expelled throughfluid outlet 570.Fluid end 540 may comprisecheck valve assemblies 580 that interface with the pistons ofpump 530, where eachcheck valve 580 is in fluid communication with bothinlet 560 andoutlet 570. Thecheck valve assemblies 580 allow fluid to be drawn only from thelow pressure inlet 560 and high pressure fluid output only throughoutlet 570. - By eliminating the need for a heavy-duty, multi-speed transmission, the variable displacement pumping system provides a smaller package for a given pump rating. The table below lists various examples of pumping systems operating at 275 revolutions per minute.
-
Plunger Max Max dia. Stroke Number Max Rate Rod load Pressure HHP inch inch Cyl bpm lbf psi 800 4.5 8 3 10.8 180000 11300 1000 4 10 3 10.7 180000 14300 2000 4.5 12 5 27.0 250000 15700 3000 5 12 3 20.0 300000 15300 - The smaller package allows higher capacity pumping systems to be mounted on chassis, trailers, or skids comparably sized to smaller pumping systems. The variable displacement pumping system also provides a more complete operating envelope as compared to conventional transmission systems.
- While exemplary embodiments of this invention have been shown and described, modifications thereof can be made by one skilled in the art without departing from the scope or teaching of this invention. The embodiments described herein are exemplary only and are not limiting. Many variations and modifications of the system and apparatus are possible and are within the scope of the invention. For example, the relative dimensions of various parts, the materials from which the various parts are made, and other parameters can be varied, so long as the apparatus retain the advantages discussed herein. Accordingly, the scope of protection is not limited to the embodiments described herein, but is only limited by the claims that follow, the scope of which shall include all equivalents of the subject matter of the claims.
Claims (20)
1. A method comprising:
operating a pumping system to provide a fluid at a pressure and a flow rate within a continuous range of pressures and flow rates between a peak horsepower and a peak torque of the pumping system;
monitoring the pressure and the flow rate of the fluid provided by the pumping system;
controlling the pumping system to provide non-discrete variations in the pressure and the flow rate of the fluid; and
pumping the fluid into a subterranean wellbore.
2. The method of claim 1 , wherein the pumping system does not comprise a transmission.
3. The method of claim 2 , wherein the pumping system comprises a pump and a motor, wherein changes in the pressure and the flow rate are controlled by varying a speed of a motor.
4. The method of claim 3 , wherein a stroke of the pump is varied by axial translation of a rotating pump shaft.
5. The method of claim 2 , wherein the pumping system comprises a pump and a motor, and wherein the pressure and the flow rate are controlled by varying a displacement of the pump.
6. The method of claim 5 , wherein a ratio of a rotational speed of the motor to a rotational speed of the pump is fixed.
7. The method of claim 5 , wherein the displacement of the pump can be adjusted by varying a stroke of the pump.
8. A method comprising:
controlling a plurality of operating parameters of a pump to provide a fluid output at any combination of pressure and flow rate within a range defined by a peak hydraulic horsepower, a peak torque, a maximum pressure, and a maximum flow rate of the pump;
monitoring the pressure and the flow rate of the fluid output; and
adjusting at least one of the operating parameters of the pump to provide a desired pressure and flow rate of the fluid output,
wherein the fluid is a wellbore servicing fluid.
9. The method of claim 8 , wherein the pump is not coupled to a transmission.
10. The method of claim 8 , wherein the adjusted operating parameter comprises a speed of the pump.
11. The method of claim 10 , wherein the speed of the pump is adjusted by adjusting the speed of a motor operating the pump.
12. The method of claim 11 , wherein the speed of the pump is related to the speed of the motor by a fixed ratio.
13. The method of claim 8 , wherein the adjusted operating parameter comprises a displacement of the pump.
14. The method of claim 13 , wherein the displacement of the pump is determined by the axial position of a rotating shaft.
15. The method of claim 14 , wherein the axial position of the rotating shaft is regulated by a displacement controller comprising a coupling engaged with the rotating shaft and a hydraulic cylinder operable to engage the coupling so as to axially translate the rotating shaft.
16. A method comprising:
operating a pumping system comprising a pump and a motor to provide a fluid at a pressure and a flow rate within a continuous range of pressures and flow rates between a peak horsepower and a peak torque of the pumping system, wherein the pumping system does not comprise a transmission; and
pumping the fluid into a subterranean wellbore.
17. The method of claim 16 , wherein the pressure and the flow rate are determined by operating parameters consisting essentially of: a displacement of the pump and a speed of the motor.
18. The method of claim 17 , wherein the displacement of the pump is determined by the axial position of a rotating shaft.
19. The method of claim 18 , wherein the axial position of the rotating shaft is regulated by a displacement controller comprising a coupling engaged with the rotating shaft and a hydraulic cylinder operable to engage the coupling so as to axially translate the rotating shaft.
20. The method of claim 16 , wherein the fluid comprises fracturing fluid, drilling mud, barite, cement, liquid CO2, or combinations thereof.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/484,961 US20090252616A1 (en) | 2004-10-27 | 2009-06-15 | Variable Rate Pumping System |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/974,437 US7563076B2 (en) | 2004-10-27 | 2004-10-27 | Variable rate pumping system |
US12/484,961 US20090252616A1 (en) | 2004-10-27 | 2009-06-15 | Variable Rate Pumping System |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/974,437 Division US7563076B2 (en) | 2004-10-27 | 2004-10-27 | Variable rate pumping system |
Publications (1)
Publication Number | Publication Date |
---|---|
US20090252616A1 true US20090252616A1 (en) | 2009-10-08 |
Family
ID=36206367
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/974,437 Active 2027-01-25 US7563076B2 (en) | 2004-10-27 | 2004-10-27 | Variable rate pumping system |
US12/484,961 Abandoned US20090252616A1 (en) | 2004-10-27 | 2009-06-15 | Variable Rate Pumping System |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/974,437 Active 2027-01-25 US7563076B2 (en) | 2004-10-27 | 2004-10-27 | Variable rate pumping system |
Country Status (1)
Country | Link |
---|---|
US (2) | US7563076B2 (en) |
Cited By (43)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080079259A1 (en) * | 2006-09-29 | 2008-04-03 | Parcell Jason W | Pump housing coupling |
CN103095209A (en) * | 2013-01-24 | 2013-05-08 | 成都宏天电传工程有限公司 | Medium-voltage frequency conversion system used for shale gas extraction |
US8621979B2 (en) | 2011-03-16 | 2014-01-07 | Halliburton Energy Services, Inc. | Lubrication system for a reciprocating apparatus |
US20150054442A1 (en) * | 2011-07-27 | 2015-02-26 | Regal Beloit America, Inc. | Methods and systems for controlling a motor |
CN104536368A (en) * | 2014-12-26 | 2015-04-22 | 四川宏华电气有限责任公司 | Electrically-driven fracturing pump power limitation protection device and method |
CN104696206A (en) * | 2015-03-02 | 2015-06-10 | 三一重型能源装备有限公司 | Fracturing truck as well as control device and method thereof |
US9079128B2 (en) | 2011-12-09 | 2015-07-14 | Hayward Industries, Inc. | Strainer basket and related methods of use |
CN107544304A (en) * | 2017-09-01 | 2018-01-05 | 三石油智能装备有限公司 | Fracturing unit truck control method and device |
WO2018101909A1 (en) * | 2016-11-29 | 2018-06-07 | Halliburton Energy Services, Inc. | Configuration and operation of an optimized pumping system |
US10227970B2 (en) | 2016-06-15 | 2019-03-12 | Schlumberger Technology Corporation | Determining pump-out flow rate |
US10718337B2 (en) | 2016-09-22 | 2020-07-21 | Hayward Industries, Inc. | Self-priming dedicated water feature pump |
US11280326B2 (en) * | 2019-06-10 | 2022-03-22 | Halliburton Energy Services, Inc. | Pump fluid end with suction valve closure assist |
US11415125B2 (en) | 2020-06-23 | 2022-08-16 | Bj Energy Solutions, Llc | Systems for utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11460368B2 (en) | 2019-09-13 | 2022-10-04 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11473413B2 (en) | 2020-06-23 | 2022-10-18 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11473503B1 (en) | 2019-09-13 | 2022-10-18 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11506040B2 (en) | 2020-06-24 | 2022-11-22 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11512570B2 (en) | 2020-06-09 | 2022-11-29 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11530602B2 (en) | 2019-09-13 | 2022-12-20 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11542802B2 (en) | 2020-06-24 | 2023-01-03 | Bj Energy Solutions, Llc | Hydraulic fracturing control assembly to detect pump cavitation or pulsation |
US11542868B2 (en) | 2020-05-15 | 2023-01-03 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11555756B2 (en) | 2019-09-13 | 2023-01-17 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11560848B2 (en) | 2019-09-13 | 2023-01-24 | Bj Energy Solutions, Llc | Methods for noise dampening and attenuation of turbine engine |
US11560845B2 (en) | 2019-05-15 | 2023-01-24 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11566506B2 (en) | 2020-06-09 | 2023-01-31 | Bj Energy Solutions, Llc | Methods for detection and mitigation of well screen out |
US11572774B2 (en) | 2020-06-22 | 2023-02-07 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11598188B2 (en) | 2020-06-22 | 2023-03-07 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US11598263B2 (en) | 2019-09-13 | 2023-03-07 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11598264B2 (en) | 2020-06-05 | 2023-03-07 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11603744B2 (en) | 2020-07-17 | 2023-03-14 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11603745B2 (en) | 2020-05-28 | 2023-03-14 | Bj Energy Solutions, Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11608725B2 (en) | 2019-09-13 | 2023-03-21 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11627683B2 (en) | 2020-06-05 | 2023-04-11 | Bj Energy Solutions, Llc | Enclosure assembly for enhanced cooling of direct drive unit and related methods |
US11624326B2 (en) | 2017-05-21 | 2023-04-11 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US11635074B2 (en) | 2020-05-12 | 2023-04-25 | Bj Energy Solutions, Llc | Cover for fluid systems and related methods |
US11639654B2 (en) | 2021-05-24 | 2023-05-02 | Bj Energy Solutions, Llc | Hydraulic fracturing pumps to enhance flow of fracturing fluid into wellheads and related methods |
US11643915B2 (en) | 2020-06-09 | 2023-05-09 | Bj Energy Solutions, Llc | Drive equipment and methods for mobile fracturing transportation platforms |
US11719234B2 (en) | 2019-09-13 | 2023-08-08 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
US11867118B2 (en) | 2019-09-13 | 2024-01-09 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US11898504B2 (en) | 2020-05-14 | 2024-02-13 | Bj Energy Solutions, Llc | Systems and methods utilizing turbine compressor discharge for hydrostatic manifold purge |
US11933153B2 (en) | 2020-06-22 | 2024-03-19 | Bj Energy Solutions, Llc | Systems and methods to operate hydraulic fracturing units using automatic flow rate and/or pressure control |
US11939853B2 (en) | 2020-06-22 | 2024-03-26 | Bj Energy Solutions, Llc | Systems and methods providing a configurable staged rate increase function to operate hydraulic fracturing units |
US11952878B2 (en) | 2022-11-30 | 2024-04-09 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
Families Citing this family (63)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7563076B2 (en) * | 2004-10-27 | 2009-07-21 | Halliburton Energy Services, Inc. | Variable rate pumping system |
US7409901B2 (en) | 2004-10-27 | 2008-08-12 | Halliburton Energy Services, Inc. | Variable stroke assembly |
US7811064B2 (en) * | 2005-08-18 | 2010-10-12 | Serva Corporation | Variable displacement reciprocating pump |
US7531092B2 (en) * | 2005-11-01 | 2009-05-12 | Hayward Industries, Inc. | Pump |
US8186517B2 (en) * | 2005-11-01 | 2012-05-29 | Hayward Industries, Inc. | Strainer housing assembly and stand for pump |
US20080264625A1 (en) * | 2007-04-26 | 2008-10-30 | Brian Ochoa | Linear electric motor for an oilfield pump |
US8069923B2 (en) * | 2008-08-12 | 2011-12-06 | Halliburton Energy Services Inc. | Top suction fluid end |
US8297920B2 (en) | 2008-11-13 | 2012-10-30 | Hayward Industries, Inc. | Booster pump system for pool applications |
US8807960B2 (en) * | 2009-06-09 | 2014-08-19 | Halliburton Energy Services, Inc. | System and method for servicing a wellbore |
US8579599B2 (en) * | 2010-03-26 | 2013-11-12 | Schlumberger Technology Corporation | System, apparatus, and method for rapid pump displacement configuration |
BR112013025880B1 (en) | 2011-04-07 | 2022-06-07 | Typhon Technology Solutions, Llc | Method for supplying fracture fluid to a wellbore and system for use in supplying pressurized fluid to a wellbore |
US9140110B2 (en) * | 2012-10-05 | 2015-09-22 | Evolution Well Services, Llc | Mobile, modular, electrically powered system for use in fracturing underground formations using liquid petroleum gas |
US11255173B2 (en) | 2011-04-07 | 2022-02-22 | Typhon Technology Solutions, Llc | Mobile, modular, electrically powered system for use in fracturing underground formations using liquid petroleum gas |
US11708752B2 (en) | 2011-04-07 | 2023-07-25 | Typhon Technology Solutions (U.S.), Llc | Multiple generator mobile electric powered fracturing system |
DE102012009136A1 (en) * | 2012-05-05 | 2013-11-07 | Robert Bosch Gmbh | Method for operating a fluid pump |
US10232332B2 (en) | 2012-11-16 | 2019-03-19 | U.S. Well Services, Inc. | Independent control of auger and hopper assembly in electric blender system |
US9650879B2 (en) | 2012-11-16 | 2017-05-16 | Us Well Services Llc | Torsional coupling for electric hydraulic fracturing fluid pumps |
US10119381B2 (en) | 2012-11-16 | 2018-11-06 | U.S. Well Services, LLC | System for reducing vibrations in a pressure pumping fleet |
US9745840B2 (en) | 2012-11-16 | 2017-08-29 | Us Well Services Llc | Electric powered pump down |
US9410410B2 (en) | 2012-11-16 | 2016-08-09 | Us Well Services Llc | System for pumping hydraulic fracturing fluid using electric pumps |
US10036238B2 (en) | 2012-11-16 | 2018-07-31 | U.S. Well Services, LLC | Cable management of electric powered hydraulic fracturing pump unit |
US10020711B2 (en) | 2012-11-16 | 2018-07-10 | U.S. Well Services, LLC | System for fueling electric powered hydraulic fracturing equipment with multiple fuel sources |
US9840901B2 (en) | 2012-11-16 | 2017-12-12 | U.S. Well Services, LLC | Remote monitoring for hydraulic fracturing equipment |
US11449018B2 (en) | 2012-11-16 | 2022-09-20 | U.S. Well Services, LLC | System and method for parallel power and blackout protection for electric powered hydraulic fracturing |
US9995218B2 (en) | 2012-11-16 | 2018-06-12 | U.S. Well Services, LLC | Turbine chilling for oil field power generation |
US10526882B2 (en) | 2012-11-16 | 2020-01-07 | U.S. Well Services, LLC | Modular remote power generation and transmission for hydraulic fracturing system |
US10254732B2 (en) | 2012-11-16 | 2019-04-09 | U.S. Well Services, Inc. | Monitoring and control of proppant storage from a datavan |
US9893500B2 (en) | 2012-11-16 | 2018-02-13 | U.S. Well Services, LLC | Switchgear load sharing for oil field equipment |
US9650871B2 (en) | 2012-11-16 | 2017-05-16 | Us Well Services Llc | Safety indicator lights for hydraulic fracturing pumps |
US10407990B2 (en) | 2012-11-16 | 2019-09-10 | U.S. Well Services, LLC | Slide out pump stand for hydraulic fracturing equipment |
US11476781B2 (en) | 2012-11-16 | 2022-10-18 | U.S. Well Services, LLC | Wireline power supply during electric powered fracturing operations |
US9611728B2 (en) | 2012-11-16 | 2017-04-04 | U.S. Well Services Llc | Cold weather package for oil field hydraulics |
US9970278B2 (en) | 2012-11-16 | 2018-05-15 | U.S. Well Services, LLC | System for centralized monitoring and control of electric powered hydraulic fracturing fleet |
US10378335B2 (en) * | 2013-03-13 | 2019-08-13 | Schlumberger Technology Corporation | Pressure testing of well servicing systems |
SG11201507126QA (en) * | 2013-03-13 | 2015-10-29 | Schlumberger Technology Bv | Pressure testing of well servicing systems |
CA2987665C (en) | 2016-12-02 | 2021-10-19 | U.S. Well Services, LLC | Constant voltage power distribution system for use with an electric hydraulic fracturing system |
US10280724B2 (en) | 2017-07-07 | 2019-05-07 | U.S. Well Services, Inc. | Hydraulic fracturing equipment with non-hydraulic power |
US11067481B2 (en) | 2017-10-05 | 2021-07-20 | U.S. Well Services, LLC | Instrumented fracturing slurry flow system and method |
US10408031B2 (en) | 2017-10-13 | 2019-09-10 | U.S. Well Services, LLC | Automated fracturing system and method |
AR114805A1 (en) | 2017-10-25 | 2020-10-21 | U S Well Services Llc | INTELLIGENT FRACTURING METHOD AND SYSTEM |
CA3084607A1 (en) | 2017-12-05 | 2019-06-13 | U.S. Well Services, LLC | High horsepower pumping configuration for an electric hydraulic fracturing system |
US10598258B2 (en) | 2017-12-05 | 2020-03-24 | U.S. Well Services, LLC | Multi-plunger pumps and associated drive systems |
AR114091A1 (en) | 2018-02-05 | 2020-07-22 | Us Well Services Inc | ELECTRICAL CHARGE MANAGEMENT IN MICROGRID |
US11035207B2 (en) | 2018-04-16 | 2021-06-15 | U.S. Well Services, LLC | Hybrid hydraulic fracturing fleet |
WO2019241783A1 (en) | 2018-06-15 | 2019-12-19 | U.S. Well Services, Inc. | Integrated mobile power unit for hydraulic fracturing |
US10648270B2 (en) | 2018-09-14 | 2020-05-12 | U.S. Well Services, LLC | Riser assist for wellsites |
US11208878B2 (en) | 2018-10-09 | 2021-12-28 | U.S. Well Services, LLC | Modular switchgear system and power distribution for electric oilfield equipment |
US11578577B2 (en) | 2019-03-20 | 2023-02-14 | U.S. Well Services, LLC | Oversized switchgear trailer for electric hydraulic fracturing |
US11728709B2 (en) | 2019-05-13 | 2023-08-15 | U.S. Well Services, LLC | Encoderless vector control for VFD in hydraulic fracturing applications |
CA3148987A1 (en) | 2019-08-01 | 2021-02-04 | U.S. Well Services, LLC | High capacity power storage system for electric hydraulic fracturing |
US11015536B2 (en) | 2019-09-13 | 2021-05-25 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US10989180B2 (en) | 2019-09-13 | 2021-04-27 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11009162B1 (en) | 2019-12-27 | 2021-05-18 | U.S. Well Services, LLC | System and method for integrated flow supply line |
US11293227B2 (en) * | 2020-02-28 | 2022-04-05 | Halliburton Energy Services, Inc. | Frac pump plunger centering bearing to avoid premature carrier, packing, or plunger failure |
US10961908B1 (en) | 2020-06-05 | 2021-03-30 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11022526B1 (en) | 2020-06-09 | 2021-06-01 | Bj Energy Solutions, Llc | Systems and methods for monitoring a condition of a fracturing component section of a hydraulic fracturing unit |
CA3179403A1 (en) | 2020-06-22 | 2021-12-30 | Edwin E. Wilson | Oilfield pressure pumping system with slow speed and high pressure fracturing fluid output |
US11193504B1 (en) | 2020-11-24 | 2021-12-07 | Aquastar Pool Products, Inc. | Centrifugal pump having a housing and a volute casing wherein the volute casing has a tear-drop shaped inner wall defined by a circular body region and a converging apex with the inner wall comprising a blocker below at least one perimeter end of one diffuser blade |
USD986289S1 (en) | 2020-11-24 | 2023-05-16 | Aquastar Pool Products, Inc. | Centrifugal pump |
USD946629S1 (en) | 2020-11-24 | 2022-03-22 | Aquastar Pool Products, Inc. | Centrifugal pump |
US20230113348A1 (en) * | 2021-10-12 | 2023-04-13 | GM Global Technology Operations LLC | Method and system with high speed motor and speed limited pump |
US11746634B2 (en) * | 2022-01-18 | 2023-09-05 | Caterpillar Inc. | Optimizing fuel consumption and emissions of a multi-rig hydraulic fracturing system |
US20230243350A1 (en) * | 2022-01-31 | 2023-08-03 | Caterpillar Inc. | Controlling ramp up of a fluid pump |
Citations (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US635258A (en) * | 1898-09-28 | 1899-10-17 | Georg Wilhelm Onken | Automatic cut-off for pumps. |
US2792156A (en) * | 1954-08-23 | 1957-05-14 | Luther S Camp | Pie filler dispenser |
US2873611A (en) * | 1955-07-01 | 1959-02-17 | Arnold E Biermann | Variable stroke mechanisms |
US3738230A (en) * | 1970-06-26 | 1973-06-12 | G Censi | Variable stroke multiple pump |
US3834839A (en) * | 1971-08-30 | 1974-09-10 | F Krebs | Metering pump |
US4028018A (en) * | 1974-06-10 | 1977-06-07 | Paterson Candy International Limited | Non-pulsing apparatus |
US4131094A (en) * | 1977-02-07 | 1978-12-26 | Crise George W | Variable displacement internal combustion engine having automatic piston stroke control |
US4188859A (en) * | 1978-09-21 | 1980-02-19 | Lamph A Norman | Fluid drive mechanisms and methods |
US4240386A (en) * | 1979-03-05 | 1980-12-23 | Oliver Crist | Variable stroke engine or compressor |
US4264281A (en) * | 1978-05-11 | 1981-04-28 | Paul Hammelmann | Pump with an automatically adjusted output rate |
US4346677A (en) * | 1980-09-02 | 1982-08-31 | Nye Norman H | Combustion engine with substantially constant compression |
US4682532A (en) * | 1985-01-07 | 1987-07-28 | Erlandson Erik E | Variable-stroke constant-compression-ratio reversible radial pump |
US4778355A (en) * | 1984-05-30 | 1988-10-18 | John And Martin Holland And Associates Limited Partnership | Well pump system |
US4830589A (en) * | 1988-09-08 | 1989-05-16 | Hypro Corp. | Variable stroke positive displacement pump |
US5136987A (en) * | 1991-06-24 | 1992-08-11 | Ford Motor Company | Variable displacement and compression ratio piston engine |
US5355632A (en) * | 1991-11-13 | 1994-10-18 | Nihon Micro Coating Co., Ltd. | Apparatus for texture processing of magnetic disk |
US5477833A (en) * | 1991-05-15 | 1995-12-26 | Orbital Engine Company (Australia) Pty. Limited | Fuel system for fuel injected internal combustion engines |
US6397794B1 (en) * | 1997-09-15 | 2002-06-04 | R. Sanderson Management, Inc. | Piston engine assembly |
US6615917B2 (en) * | 1997-07-09 | 2003-09-09 | Baker Hughes Incorporated | Computer controlled injection wells |
US6715995B2 (en) * | 2002-01-31 | 2004-04-06 | Visteon Global Technologies, Inc. | Hybrid compressor control method |
US6742441B1 (en) * | 2002-12-05 | 2004-06-01 | Halliburton Energy Services, Inc. | Continuously variable displacement pump with predefined unswept volume |
US6976831B2 (en) * | 2003-06-25 | 2005-12-20 | Halliburton Energy Services, Inc. | Transmissionless variable output pumping unit |
US7140343B2 (en) * | 2002-05-28 | 2006-11-28 | R. Sanderson Management, Inc. | Overload protection mechanism |
US7409901B2 (en) * | 2004-10-27 | 2008-08-12 | Halliburton Energy Services, Inc. | Variable stroke assembly |
US7563076B2 (en) * | 2004-10-27 | 2009-07-21 | Halliburton Energy Services, Inc. | Variable rate pumping system |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5335632A (en) | 1993-05-14 | 1994-08-09 | Hefley Carl D | Variable compression internal combustion engine |
-
2004
- 2004-10-27 US US10/974,437 patent/US7563076B2/en active Active
-
2009
- 2009-06-15 US US12/484,961 patent/US20090252616A1/en not_active Abandoned
Patent Citations (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US635258A (en) * | 1898-09-28 | 1899-10-17 | Georg Wilhelm Onken | Automatic cut-off for pumps. |
US2792156A (en) * | 1954-08-23 | 1957-05-14 | Luther S Camp | Pie filler dispenser |
US2873611A (en) * | 1955-07-01 | 1959-02-17 | Arnold E Biermann | Variable stroke mechanisms |
US3738230A (en) * | 1970-06-26 | 1973-06-12 | G Censi | Variable stroke multiple pump |
US3834839A (en) * | 1971-08-30 | 1974-09-10 | F Krebs | Metering pump |
US4028018A (en) * | 1974-06-10 | 1977-06-07 | Paterson Candy International Limited | Non-pulsing apparatus |
US4131094A (en) * | 1977-02-07 | 1978-12-26 | Crise George W | Variable displacement internal combustion engine having automatic piston stroke control |
US4264281A (en) * | 1978-05-11 | 1981-04-28 | Paul Hammelmann | Pump with an automatically adjusted output rate |
US4188859A (en) * | 1978-09-21 | 1980-02-19 | Lamph A Norman | Fluid drive mechanisms and methods |
US4240386A (en) * | 1979-03-05 | 1980-12-23 | Oliver Crist | Variable stroke engine or compressor |
US4346677A (en) * | 1980-09-02 | 1982-08-31 | Nye Norman H | Combustion engine with substantially constant compression |
US4778355A (en) * | 1984-05-30 | 1988-10-18 | John And Martin Holland And Associates Limited Partnership | Well pump system |
US4682532A (en) * | 1985-01-07 | 1987-07-28 | Erlandson Erik E | Variable-stroke constant-compression-ratio reversible radial pump |
US4830589A (en) * | 1988-09-08 | 1989-05-16 | Hypro Corp. | Variable stroke positive displacement pump |
US5477833A (en) * | 1991-05-15 | 1995-12-26 | Orbital Engine Company (Australia) Pty. Limited | Fuel system for fuel injected internal combustion engines |
US5136987A (en) * | 1991-06-24 | 1992-08-11 | Ford Motor Company | Variable displacement and compression ratio piston engine |
US5355632A (en) * | 1991-11-13 | 1994-10-18 | Nihon Micro Coating Co., Ltd. | Apparatus for texture processing of magnetic disk |
US6615917B2 (en) * | 1997-07-09 | 2003-09-09 | Baker Hughes Incorporated | Computer controlled injection wells |
US6446587B1 (en) * | 1997-09-15 | 2002-09-10 | R. Sanderson Management, Inc. | Piston engine assembly |
US6397794B1 (en) * | 1997-09-15 | 2002-06-04 | R. Sanderson Management, Inc. | Piston engine assembly |
US6715995B2 (en) * | 2002-01-31 | 2004-04-06 | Visteon Global Technologies, Inc. | Hybrid compressor control method |
US7140343B2 (en) * | 2002-05-28 | 2006-11-28 | R. Sanderson Management, Inc. | Overload protection mechanism |
US6742441B1 (en) * | 2002-12-05 | 2004-06-01 | Halliburton Energy Services, Inc. | Continuously variable displacement pump with predefined unswept volume |
US6976831B2 (en) * | 2003-06-25 | 2005-12-20 | Halliburton Energy Services, Inc. | Transmissionless variable output pumping unit |
US7409901B2 (en) * | 2004-10-27 | 2008-08-12 | Halliburton Energy Services, Inc. | Variable stroke assembly |
US7563076B2 (en) * | 2004-10-27 | 2009-07-21 | Halliburton Energy Services, Inc. | Variable rate pumping system |
Cited By (90)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8182212B2 (en) | 2006-09-29 | 2012-05-22 | Hayward Industries, Inc. | Pump housing coupling |
US20080079259A1 (en) * | 2006-09-29 | 2008-04-03 | Parcell Jason W | Pump housing coupling |
US8621979B2 (en) | 2011-03-16 | 2014-01-07 | Halliburton Energy Services, Inc. | Lubrication system for a reciprocating apparatus |
US20150054442A1 (en) * | 2011-07-27 | 2015-02-26 | Regal Beloit America, Inc. | Methods and systems for controlling a motor |
US9079128B2 (en) | 2011-12-09 | 2015-07-14 | Hayward Industries, Inc. | Strainer basket and related methods of use |
CN103095209A (en) * | 2013-01-24 | 2013-05-08 | 成都宏天电传工程有限公司 | Medium-voltage frequency conversion system used for shale gas extraction |
CN104536368A (en) * | 2014-12-26 | 2015-04-22 | 四川宏华电气有限责任公司 | Electrically-driven fracturing pump power limitation protection device and method |
CN104696206A (en) * | 2015-03-02 | 2015-06-10 | 三一重型能源装备有限公司 | Fracturing truck as well as control device and method thereof |
US10227970B2 (en) | 2016-06-15 | 2019-03-12 | Schlumberger Technology Corporation | Determining pump-out flow rate |
US10718337B2 (en) | 2016-09-22 | 2020-07-21 | Hayward Industries, Inc. | Self-priming dedicated water feature pump |
WO2018101909A1 (en) * | 2016-11-29 | 2018-06-07 | Halliburton Energy Services, Inc. | Configuration and operation of an optimized pumping system |
US11339776B2 (en) | 2016-11-29 | 2022-05-24 | Halliburton Energy Services, Inc. | Configuration and operation of an optimized pumping system |
US11624326B2 (en) | 2017-05-21 | 2023-04-11 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
CN107544304A (en) * | 2017-09-01 | 2018-01-05 | 三石油智能装备有限公司 | Fracturing unit truck control method and device |
US11560845B2 (en) | 2019-05-15 | 2023-01-24 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11280326B2 (en) * | 2019-06-10 | 2022-03-22 | Halliburton Energy Services, Inc. | Pump fluid end with suction valve closure assist |
US11885316B2 (en) | 2019-06-10 | 2024-01-30 | Halliburton Energy Services, Inc. | Pump fluid end with suction valve closure assist |
US11619122B2 (en) | 2019-09-13 | 2023-04-04 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11604113B2 (en) | 2019-09-13 | 2023-03-14 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11473997B2 (en) | 2019-09-13 | 2022-10-18 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11473503B1 (en) | 2019-09-13 | 2022-10-18 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11867118B2 (en) | 2019-09-13 | 2024-01-09 | Bj Energy Solutions, Llc | Methods and systems for supplying fuel to gas turbine engines |
US11719234B2 (en) | 2019-09-13 | 2023-08-08 | Bj Energy Solutions, Llc | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
US11512642B1 (en) | 2019-09-13 | 2022-11-29 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11655763B1 (en) | 2019-09-13 | 2023-05-23 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11530602B2 (en) | 2019-09-13 | 2022-12-20 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11859482B2 (en) | 2019-09-13 | 2024-01-02 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11649766B1 (en) | 2019-09-13 | 2023-05-16 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11555756B2 (en) | 2019-09-13 | 2023-01-17 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11560848B2 (en) | 2019-09-13 | 2023-01-24 | Bj Energy Solutions, Llc | Methods for noise dampening and attenuation of turbine engine |
US11460368B2 (en) | 2019-09-13 | 2022-10-04 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11725583B2 (en) | 2019-09-13 | 2023-08-15 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11852001B2 (en) | 2019-09-13 | 2023-12-26 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11629584B2 (en) | 2019-09-13 | 2023-04-18 | Bj Energy Solutions, Llc | Power sources and transmission networks for auxiliary equipment onboard hydraulic fracturing units and associated methods |
US11578660B1 (en) | 2019-09-13 | 2023-02-14 | Bj Energy Solutions, Llc | Direct drive unit removal system and associated methods |
US11767791B2 (en) | 2019-09-13 | 2023-09-26 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11598263B2 (en) | 2019-09-13 | 2023-03-07 | Bj Energy Solutions, Llc | Mobile gas turbine inlet air conditioning system and associated methods |
US11613980B2 (en) | 2019-09-13 | 2023-03-28 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11608725B2 (en) | 2019-09-13 | 2023-03-21 | Bj Energy Solutions, Llc | Methods and systems for operating a fleet of pumps |
US11761846B2 (en) | 2019-09-13 | 2023-09-19 | Bj Energy Solutions, Llc | Fuel, communications, and power connection systems and related methods |
US11708829B2 (en) | 2020-05-12 | 2023-07-25 | Bj Energy Solutions, Llc | Cover for fluid systems and related methods |
US11635074B2 (en) | 2020-05-12 | 2023-04-25 | Bj Energy Solutions, Llc | Cover for fluid systems and related methods |
US11898504B2 (en) | 2020-05-14 | 2024-02-13 | Bj Energy Solutions, Llc | Systems and methods utilizing turbine compressor discharge for hydrostatic manifold purge |
US11542868B2 (en) | 2020-05-15 | 2023-01-03 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11624321B2 (en) | 2020-05-15 | 2023-04-11 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11698028B2 (en) | 2020-05-15 | 2023-07-11 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
US11603745B2 (en) | 2020-05-28 | 2023-03-14 | Bj Energy Solutions, Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11814940B2 (en) | 2020-05-28 | 2023-11-14 | Bj Energy Solutions Llc | Bi-fuel reciprocating engine to power direct drive turbine fracturing pumps onboard auxiliary systems and related methods |
US11723171B2 (en) | 2020-06-05 | 2023-08-08 | Bj Energy Solutions, Llc | Enclosure assembly for enhanced cooling of direct drive unit and related methods |
US11746698B2 (en) | 2020-06-05 | 2023-09-05 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11627683B2 (en) | 2020-06-05 | 2023-04-11 | Bj Energy Solutions, Llc | Enclosure assembly for enhanced cooling of direct drive unit and related methods |
US11598264B2 (en) | 2020-06-05 | 2023-03-07 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11891952B2 (en) | 2020-06-05 | 2024-02-06 | Bj Energy Solutions, Llc | Systems and methods to enhance intake air flow to a gas turbine engine of a hydraulic fracturing unit |
US11629583B2 (en) | 2020-06-09 | 2023-04-18 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US20230086213A1 (en) * | 2020-06-09 | 2023-03-23 | Bj Energy Solutions, Llc | Methods for detection and mitigation of well screen out |
US11939854B2 (en) * | 2020-06-09 | 2024-03-26 | Bj Energy Solutions, Llc | Methods for detection and mitigation of well screen out |
US11566506B2 (en) | 2020-06-09 | 2023-01-31 | Bj Energy Solutions, Llc | Methods for detection and mitigation of well screen out |
US11643915B2 (en) | 2020-06-09 | 2023-05-09 | Bj Energy Solutions, Llc | Drive equipment and methods for mobile fracturing transportation platforms |
US11512570B2 (en) | 2020-06-09 | 2022-11-29 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11867046B2 (en) | 2020-06-09 | 2024-01-09 | Bj Energy Solutions, Llc | Systems and methods for exchanging fracturing components of a hydraulic fracturing unit |
US11732565B2 (en) | 2020-06-22 | 2023-08-22 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11933153B2 (en) | 2020-06-22 | 2024-03-19 | Bj Energy Solutions, Llc | Systems and methods to operate hydraulic fracturing units using automatic flow rate and/or pressure control |
US11939853B2 (en) | 2020-06-22 | 2024-03-26 | Bj Energy Solutions, Llc | Systems and methods providing a configurable staged rate increase function to operate hydraulic fracturing units |
US11572774B2 (en) | 2020-06-22 | 2023-02-07 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11598188B2 (en) | 2020-06-22 | 2023-03-07 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US11898429B2 (en) | 2020-06-22 | 2024-02-13 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11639655B2 (en) | 2020-06-22 | 2023-05-02 | Bj Energy Solutions, Llc | Systems and methods to operate a dual-shaft gas turbine engine for hydraulic fracturing |
US11649820B2 (en) | 2020-06-23 | 2023-05-16 | Bj Energy Solutions, Llc | Systems and methods of utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11415125B2 (en) | 2020-06-23 | 2022-08-16 | Bj Energy Solutions, Llc | Systems for utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11939974B2 (en) | 2020-06-23 | 2024-03-26 | Bj Energy Solutions, Llc | Systems and methods of utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11719085B1 (en) | 2020-06-23 | 2023-08-08 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11428218B2 (en) | 2020-06-23 | 2022-08-30 | Bj Energy Solutions, Llc | Systems and methods of utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11473413B2 (en) | 2020-06-23 | 2022-10-18 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11661832B2 (en) | 2020-06-23 | 2023-05-30 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11566505B2 (en) | 2020-06-23 | 2023-01-31 | Bj Energy Solutions, Llc | Systems and methods to autonomously operate hydraulic fracturing units |
US11466680B2 (en) | 2020-06-23 | 2022-10-11 | Bj Energy Solutions, Llc | Systems and methods of utilization of a hydraulic fracturing unit profile to operate hydraulic fracturing units |
US11542802B2 (en) | 2020-06-24 | 2023-01-03 | Bj Energy Solutions, Llc | Hydraulic fracturing control assembly to detect pump cavitation or pulsation |
US11746638B2 (en) | 2020-06-24 | 2023-09-05 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11506040B2 (en) | 2020-06-24 | 2022-11-22 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11512571B2 (en) | 2020-06-24 | 2022-11-29 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11692422B2 (en) | 2020-06-24 | 2023-07-04 | Bj Energy Solutions, Llc | System to monitor cavitation or pulsation events during a hydraulic fracturing operation |
US11668175B2 (en) | 2020-06-24 | 2023-06-06 | Bj Energy Solutions, Llc | Automated diagnostics of electronic instrumentation in a system for fracturing a well and associated methods |
US11920450B2 (en) | 2020-07-17 | 2024-03-05 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11608727B2 (en) | 2020-07-17 | 2023-03-21 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11603744B2 (en) | 2020-07-17 | 2023-03-14 | Bj Energy Solutions, Llc | Methods, systems, and devices to enhance fracturing fluid delivery to subsurface formations during high-pressure fracturing operations |
US11867045B2 (en) | 2021-05-24 | 2024-01-09 | Bj Energy Solutions, Llc | Hydraulic fracturing pumps to enhance flow of fracturing fluid into wellheads and related methods |
US11732563B2 (en) | 2021-05-24 | 2023-08-22 | Bj Energy Solutions, Llc | Hydraulic fracturing pumps to enhance flow of fracturing fluid into wellheads and related methods |
US11639654B2 (en) | 2021-05-24 | 2023-05-02 | Bj Energy Solutions, Llc | Hydraulic fracturing pumps to enhance flow of fracturing fluid into wellheads and related methods |
US11952878B2 (en) | 2022-11-30 | 2024-04-09 | Bj Energy Solutions, Llc | Stage profiles for operations of hydraulic systems and associated methods |
US11959419B2 (en) | 2023-05-10 | 2024-04-16 | Bj Energy Solutions, Llc | Onboard heater of auxiliary systems using exhaust gases and associated methods |
Also Published As
Publication number | Publication date |
---|---|
US7563076B2 (en) | 2009-07-21 |
US20060088423A1 (en) | 2006-04-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7563076B2 (en) | Variable rate pumping system | |
US5616009A (en) | Mud pump | |
AU2008286752B2 (en) | Hybrid hydraulic-electric ram pumping unit with downstroke energy recovery | |
US4474002A (en) | Hydraulic drive pump apparatus | |
KR100350194B1 (en) | Variable Displacement Axial Piston Hydraulic Unit | |
US10352138B2 (en) | Lift apparatus for driving a downhole reciprocating pump | |
EP2414680B1 (en) | High pressure variable displacement piston pump | |
Achten et al. | Valving land phenomena of the innas hydraulic transformer | |
US4790728A (en) | Dual-rigid-hollow-stem actuators in opposite-phase slurry pump drive having variable pumping speed and force | |
US10612531B2 (en) | Hydraulically-driven double-acting mud pump | |
US11761317B2 (en) | Decoupled long stroke pump | |
WO1998036172A1 (en) | High pressure pump | |
US5145332A (en) | Well pumping | |
US5827051A (en) | Regenerative hydraulic power transmission for down-hole pump | |
CA1212313A (en) | Hydraulic well pump | |
US20060120882A1 (en) | Motor or pump assemblies | |
CA1255966A (en) | Mud pump | |
US5207726A (en) | Hydraulic pump | |
CN1237254C (en) | Mud circulation system | |
CN2555386Y (en) | Slarry cycling appts. | |
KR101861076B1 (en) | Apparatus for controlling the flow rate of pump provided in electric hydrostatic system | |
WO2020161237A1 (en) | Fluid pump, pump assembly and method of pumping fluid | |
JPH10281056A (en) | High pressure pump | |
CN112814964A (en) | Valveless reversing device and method | |
CA2382668A1 (en) | Fluid driven mud pump |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: HALLIBURTON ENERGY SERVICES, INC.,TEXAS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BRUNET, JOHN DEXTER;STRIBLING, DAVID MARK;DEAN, TODD J.;AND OTHERS;SIGNING DATES FROM 20041021 TO 20041026;REEL/FRAME:024168/0117 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |