• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Summary "Apparatus and method of referencing a pumping rod pump" A method and system is provided for determining the position of a pumping rod pumping system without a position sensing device during production pumping. a pump control system of the pump rod pumping system includes a database coupled controller, with the controller configured to access a rxless torque value in the database. With the stored rxless torque value representative of crank arm points and pivot during an initial calibration pumping cycle, the controller is additionally configured to continuously sample the system rxless torque value and determine the crank arm position relative to to the sample rxless torque value. The controller adjusts the pumping system for optimal operations without a crank arm position sensor during production pumping by identifying a pivot point and adjusting the crank arm position estimate equal to the value corresponding to the crank position at the point. of articulation identified.
    公开号:BR112015010330B1
    申请号:R112015010330-8
    申请日:2013-11-04
    公开日:2018-04-03
    发明作者:G. Peterson Ronald
    申请人:Unico, Inc.；
    IPC主号:
    专利说明:

    (54) Title: METHOD FOR DETERMINING THE POSITION OF A PUMP ROD PUMPING SYSTEM AND PUMP CONTROL SYSTEM (73) Holder: UNICO, INC .. Address: 3745 NICHOLSON ROAD, FRANKSVILLE, UNITED STATES OF AMERICA (US) , 531260505 (72) Inventor: RONALD G. PETERSON
    Validity Term: 20 (twenty) years from 11/04/2013, observing the legal conditions
    Issued on: 03/04/2018
    Digitally signed by:
    Júlio César Castelo Branco Reis Moreira
    Patent Director
    1/21
    METHOD FOR DETERMINING THE POSITION OF A PUMP ROD PUMPING SYSTEM AND PUMP CONTROL SYSTEM
    REMISSIVE REFERENCE TO RELATED PATENT APPLICATIONS [001] This application is a non-provisional application claiming priority to provisional application serial number 61 / 722.8844 filed on November 6, 2012, which is incorporated here, in full, by that reference.
    FIELD OF THE INVENTION [002] The present disclosure relates generally to the control of pumping rod pumps for oil, gas and water wells, and more particularly to an apparatus and methods for determining the position of a pumping rod pumping system. without a position detection device during production pumping to optimize the operation of the stem pump.
    BACKGROUND OF THE INVENTION [003] A reciprocating pumping rod pumping unit for a rod column to drive an underground pump for the purpose of lifting liquids to the surface. An exemplary modality is shown in figure 1. Such units are often instrumented with various sensors attached to the pumping unit for the purpose of tracking well and pump performance. Historically, this instrumentation has included sensors such as (but not limited to) rod load cell, crank position sensor, motor position sensor, motor voltage / current sensors and beam inclinometer.
    [004] In addition to the performance of the tracking system, these sensors can also be used to optimize or optimize the operation of the pumping system, maximize production rates and / or protect pumping equipment. For example, feedback information from sensors allows the generation of “dynamometer graphs” (pump load versus position data) that
    Petition 870180011356, of 02/09/2018, p. 6/33
    2/21 can be used to infer valuable downhole conditions such as pump load, pump flow rate, well inflow, and pump health, which can in turn be used to optimize or optimize the operation of the pumping system.
    [005] Sensors externally attached to a pumping unit add additional cost, represent a potential failure mode, require frequent maintenance, and are often not functional due to poor maintenance or neglect. Failure of these devices, especially in remotely located areas, can cause the pumping system to operate below optimum, possibly impairing production rates and / or causing damage to the pumping system.
    [006] US patent 7,168,924 describes a method by which the rod load cell sensor can be eliminated, thereby providing a cheaper and more reliable system. The ‘924 patent is assigned to the assignee of that order and is incorporated here, in its entirety, as if fully exposed here. However, a positioning sensor of some kind is still required to reference the absolute position of the pumping unit. This can include a crank position sensor (a discreetly activated sensor or switch attached to the pumping unit crank arm), an inclinometer attached to the main beam of the pumping unit (also referred to as a rocker), or any other such method to determine the crank position with an externally mounted “reference” device.
    [007] The apparatus of the present disclosure must also be of construction that is both durable and of long duration, and must also require that little or no maintenance is provided by the user during its entire operational life. In order to increase the market appeal of the apparatus of the present disclosure, it must also be of cheap construction to thereby supply the broader market
    Petition 870180011356, of 02/09/2018, p. 7/33
    3/21 possible. Finally, it is also an objective that all the advantages and objectives mentioned above are obtained without incurring any substantial relative disadvantage.
    SUMMARY OF THE INVENTION [008] The disadvantages and limitations of the prior art discussed above are overcome by the present disclosure.
    [009] A method and system for determining the position of a pumping rod pumping system without a position detector device during production pumping is provided. The pumping system includes a stem column carrying a downhole pump, a variable drive coupled to the stem column for reciprocating movement of the stem column in a well hole and operation of the pump. A crank arm, with a counterweight, is coupled to a main beam with a steering and motor lever. The motor is coupled to a controller.
    [010] The method includes performing an initial embedding procedure to determine an rxless torque value at crank arm pivot points during an initial calibration pumping cycle. The rxless torque value is measured and stored in a database attached to the controller. During normal production pumping operation the controller continuously samples the rxless torque and determines the position of the crank arm in relation to the sample rxless torque value. The controller compares the sample rxless torque value with the stored rxless torque value and determines two of the sampled rxless torque values that correspond to the rxless torque values stored by the crank arm pivot points.
    [011] The controller adjusts the pumping system for optimal operation of the pumping system without a crank arm position sensor during pumping production by identifying a pivot point and adjusting the stipulation 870180011356, from 02/09/2018, pg . 8/33
    4/21 crank arm position equals the value corresponding to the crank position at that point of articulation.
    [012] In one embodiment, the method includes defining an articulation point as one of an upper dead center and the lower dead center position of the main beam when the stem column is in a maximum and minimum extended position, respectively. In another embodiment, the method includes determining the rxless forque derivative and storing the derivative in the database. Each pivot point has an associated rxless torque derivative.
    [013] A pump control system is also provided to control the performance of a pumping rod pump system during pumping production from a well. The pumping rod pumping system includes a rod column carrying a downhole pump, a variable drive coupled to the rod column for reciprocating movement of the rod column in a borehole and pump operation. A crank arm, with a counterweight, is coupled to a main beam with a steering lever.
    [014] A pump control system for the pumping rod pumping system includes a controller coupled to a database, with the controller configured to access a rxless torque value in the database. With the stored rxless torque value representative of crank arm pivot points during an initial calibration pumping cycle, the controller is further configured to continuously sample the system's rxless torque value and determine the crank arm position relative to to the sample rxless torque value. The system also includes a motor coupled to the steering lever and the crank arm, with the motor performance controlled by the controller based on a comparison, by the controller, of the sampled rxless shift value with the stored rxless torque value. An identification is made of two of the sampled rxless torque values that correspond to the weapon rxless torque values. Petition 870180011356, of 02/09/2018, p. 9/33
    5/21 zenous spaced by the crank arm articulation points. The controller then adjusts the motor, speed or torque by the controller to adjust the crank arm position at a pivot point for optimal system operation and pumping without a crank arm position sensor during production pumping. In another embodiment, the pump control system includes configuring the controller to define a pivot point as one of an upper dead center and lower dead center position of the main beam when the stem column is in, respectively, maximum extended position and minimum. In an additional embodiment, the pump control system is configured in such a way that the relationship between the crank arm counterweight and the steering lever pivot is asymmetrical.
    [015] The apparatus of the present invention is of a construction that is both durable and long lasting, and which will require that little or no maintenance is provided by the user throughout its operational lifetime. Finally, all the advantages and objectives mentioned above are obtained without incurring any substantial relative disadvantage.
    DESCRIPTION OF THE DRAWINGS [016] These and other advantages of the present disclosure are best understood with reference to the drawings in which:
    [017] Figure 1 is a representation of a pump rod pump system including a controller, computer and data bank configured to execute the revealed method to optimize the operation of the pump system for production pumping without an arm position crank.
    [018] Figure 2 is a schematic illustration of the pump system illustrated in Figure 1 and to identify various geometric relationships.
    [019] Figure 3 is an equation, using the geometric relation identified in figure 2, to determine, on the controller computer illustrated in figure 1, an angle
    Petition 870180011356, of 02/09/2018, p. 10/33
    6/21 of crank arm where a maximum and minimum position of the main beam of the pumping system, corresponding to a point of articulation of a position of crank arm in a position of upward and downward stroke of the main beam.
    [020] Figure 4 is a flow chart of an initial incorporation process for the pumping system according to this disclosure.
    [021] Figure 5 is a flow chart of a production (normal) pumping mode of the pump rod and pump illustrated in figure 1, without a crank arm position sensor.
    [022] Figure 6 is an exemplary graph of identification of the pivot point when plotting the rod speed against the crank arm angle.
    [023] Figure 7 is an exemplary graph of identification of the pivot point when plotting the position of the stem against the angle of the crank arm.
    [024] Figure 8 is an exemplary graph identifying an rxless torque value during an upward and downward stroke of the main beam of the pump system during production pumping.
    [025] Figure 9 is an exemplary graph illustrating an rxless torque value and the FALL rule that correspond to the absolute crank arm position determined by the method disclosed here.
    [026] Figure 10 is an exemplary graph of a dynamometer graph, generated by the method revealed here without external mounted sensors attached to the pumping system illustrated in figure 1, and used to control the pump system for optimal production operation.
    DETAILED DESCRIPTION OF EXEMPLARY MODALITIES [027] Pumping rod pumping units are typically driven by an electric motor as the main motor. According to the present disclosure a user is able to determine the crank position of the pump unit. Petition 870180011356, from 02/09/2018, p. 11/33
    7/21 ment (and therefore the absolute position reference) directly from the main motor motor torque and speed (derived from the motor current and voltage). After the absolute position of the crank and main beam is determined, the position of the pumping rod can subsequently be determined using information about the specific pump unit (as described below), where the position of the rod is proportional to the angle of the main beam times the total stem stroke.
    [028] The preferred mode uses a system identification routine during initial calibration (also referred to as embedding) to identify the rotating inertia of the system, comprising the crank arm, gearbox, pulleys and armature of the main motor motor. This routine is initially performed during pump incorporation with an inclinometer (or some other absolute positioning device) temporarily attached to the pumping unit. Such incorporation of the system is done in a calibration pump cycle. The initial calibration procedure identifies and characterizes system parameters. During this routine, the rotating inertia of the pumping unit is characterized and levels of “articulation point” torques of the upward stroke and normalized downward stroke are stored, as described below. Alternatively, the rotating inertia can be pre-established or calculated by any means other than the system identification routine. The inclinometer device is subsequently removed and the system is operated on a production pump cycle without sensors in the pump frame or downhole in the downhole.
    [029] With reference to figure 1, a pumping rod pump system 104 is shown, the operation of which is controlled by a rod pump control system and method including a parameter estimator according to the present invention. For purposes of illustration, the stem pump control system 122 is described with reference to an application in a stem pump system 104 that
    Petition 870180011356, of 02/09/2018, p. 12/33
    8/21 includes a conventional beam pump. The beam pump has a rocker arm 138 that reciprocates a stem column 144 that includes a portion of polished stem 146. The stem column 144 is suspended from the beam to drive a downhole pump 110 which is arranged on the bottom of a well 112. However, the rod pump control system and method provided by the invention are applicable to any system that uses an electric motor to reciprocate a rod column, including those that drive the rod through belt or chain drives . For example, a belt driven pumping unit includes a belt that is attached to a stem column to reciprocate the stem column vertically in a well as the belt is driven by an engine.
    [030] The rocker 138, in turn, is driven by the steering lever 31, which is reciprocated by a crank arm 134 driven by an electric motor 130 that is coupled to the crank arm 134 through an ax reduction mechanism, like a gearbox 132. The typical motor 130 can be a three-phase AC induction motor operable at 460 VAC and developing 10 125 horsepower, depending on the capacity and depth of the pump. Other types of motors such as synchronous motors can be used to drive the pumping unit. Gearbox 132 converts engine torque at a low speed, but outputs a high torque to drive crank arm 134. Crank arm 134 is provided with a counterweight 142 that serves to balance stem column 144 suspended from beam 138 in the manner known in the art. Counterbalance can also be provided by an air cylinder like those found in air balanced units. Belt pumping and units can use a counterweight that extends in the opposite direction of the stem stroke.
    [031] The downhole pump 110 is a reciprocating type pump having a plunger 116 attached to the end of the stem column 144 and a pump cylinder 114 which is attached to the tubing end in well 100. The plunger 116
    Petition 870180011356, of 02/09/2018, p. 13/33
    9/21 includes a displacement valve 118 and a stationary valve 120 positioned at the bottom of cylinder 114. In the upward stroke of the pump, displacement valve 118 closes and raises fluid, such as oil and / or water, above piston 116 to the top of the well and stationary valve 120 opens and allows additional fluid from the reservoir to flow into pump cylinder 114. In the downward stroke, displacement valve 118 opens and stationary valve 120 closes in preparation for the next cycle. The operation of the pump 100 is controlled so that the level and fluid maintained in the pump cylinder 114 is sufficient to keep the lower end of the stem column 144 in the fluid over its entire stroke.
    [032] In one embodiment, instantaneous motor currents and voltages together with pump parameters are used to determine the rod and load position without the need for tension gauges, load cells or position sensors as well as determining pump pressure and pump flow without the need for additional surface or downhole sensors. The rod and load position can be used to control the operation of the pump 110 to optimize the operation of the pump 110. In addition, specifications from the American Petroleum Institute (API) were used to define the pump geometry that allows the use of data readily available from manufacturers and pump. System identification routines are used to establish specific installation-dependent parameters for the specific pump used in the calculation of performance parameters that are used in closed-loop control in real time of pump and stem operation, avoiding the need to create large queries for parameter values used in calculating performance parameters.
    [033] The pump control system 104 includes transducers, such as voltage and current sensors, to detect dynamic variables associated with motor torque and speed. Current sensors are coupled to a sufficient number of motor cables for the type of motor used. Current sensors provide feedbackPetition 870180011356, from 02/09/2018, p. 14/33
    10/21 gens proportional to the instantaneous stator currents in the motor 130. Voltage sensors are connected through a sufficient number of the motor windings for the type of motor used and provide voltages proportional to the instantaneous voltages through the motor windings. The current and voltage signals produced by sensors are supplied to a processor 124 through suitable input / output devices. Processor 124 further includes processing unit 126 and storage devices 128 that store programs and data files used in calculating operating parameters and producing control signals to control the operation of the stem pump system 104. This control arrangement provides near-instant readings and torque motor speed that can be used for real-time closed-loop monitoring and control of the stem pump. For example, in one mode, motor speed and torque computations used for real-time closed loop control are provided at the rate of 1000 times per second.
    [034] Motor currents and voltages are detected to determine the level and instantaneous electrical energy extracted from the power source by the electric motor operating the well pump. As the stem column 144 that drives the downhole pump 110 is raised and lowered during each cycle, the motor 130 is cyclically loaded. Depending on the specific pump installation configuration, rocker 139 is in a known position during maximum and minimum motor loads. The timing of these minimums and maximums can define the operating pumping frequency and, by integrating the motor speed into the motor light for crank gears, it is possible to estimate the phase position of the pump crank at any time. By monitoring variances in motor currents and voltages as a function of pump crank angle, voltage and current variances can be used together with parameters related to pump geometry to calculate rod position and rod load estimates.
    Petition 870180011356, of 02/09/2018, p. 15/33
    11/21 [035] The apparatus and method described above apply to the control of traditional pump jack “pump jacks” with “crank arm” counterbalance mechanism as shown in figure 1. The “crank swing” aspect refers to rotary counterweight 142 mounted on crank arm 134. In some configurations there may be two crank arms and counterweights.
    [036] This disclosure allows a pumping controller and pumping rod 124 to generate “dynamometer graphics”, as shown in figure 10, without the need for externally mounted sensors attached to the pumping unit. Controller 124 can, in turn, use dynamometer graphs to automatically adjust any pumping system parameters such as main motor speed, torque or power to optimize or optimize the operation of the pumping system. For example, oil production can be increased, the oil reservoir better controlled to promote higher final recovery, and / or increased pumping equipment life by eliminating pump rod and fluid lake warpage, in turn reducing pipeline wear and associated maintenance costs and production losses from downtime.
    [037] Controller 124 should generate a value representative of the position of the pumping unit, such as the angle of the crank arm 134. According to the disclosure, the angle of the crank arm can be periodically determined by analyzing the coupled motor torque. knowledge of the geometry of the pumping unit, specifically the “pivot points” of the pumping unit. The pivot points are defined as the “top dead center” and “bottom dead center” positions of the main beam 138 pumping unit, where the stem is in its maximum and minimum extended positions, as the “torque factor” (as known in the art) passes through zero. Figures 6 and 7 illustrate the points of articulation. Figure 6 is a graph illustrating the points of articulation
    Petition 870180011356, of 02/09/2018, p. 16/33
    12/21 when plotting rod speed against crank angle. Figure 7 is a graph illustrating the points of articulation when tracing the position of the rod against the crank angle.
    [038] The pivot points represent unique singularities during the stroke of polished rod 146, providing small “windows” that controller 124 can use to identify the position of crank arm 134 from the crank torque value. As the pumping unit passes through its pivot points, the crank torque (and therefore motor torque) is totally decoupled from the complex effects of the stem load. At the pivot points, the motor torque is influenced only by the effects of motor 130 and rotary inertia of the pumping unit, counterweight effect of the pumping unit, and rotary friction, all of which can be properly estimated and therefore predicted or measured after initial incorporation. In addition, these "windows" occur at regular intervals, and the relative distance between the intervals can be analytically predetermined given the geometry of the pumping unit.
    [039] During portions of the pumping unit cycle other than its pivot points, the motor torque is influenced by several confusing factors. If a person tried to determine the crank position (reference to the pumping unit) based on the analysis of the motor torque during any portion of the cycle other than the pivot points, the complexity of the aforementioned influences would make the technique unsustainable. As such, it is extremely difficult to correlate the motor torque with the motor position at any point during the cycle other than the unit pivot points (where the expected torque is most highly predictable).
    [040] Explaining about this point follows a list of the various forces that contribute to the torque observed in the main engine 130, comprising:
    Petition 870180011356, of 02/09/2018, p. 17/33
    13/21 [041]. downhole pump liquid load (the weight of the liquid column acting on the pump plunger) [042]. stem weight (the weight of the pumping rods) [043]. pumping unit counterbalance torque [044]. pumping unit rotary inertia [045]. pumping unit articulation inertia [046]. friction (pump, rod, seal box, pumping unit, gear box, etc.).
    [047] The various forces listed above are translated back to motor 130, as a torque, through the geometry of the pumping unit. The geometry of the pumping unit mechanism (see figure 2) affects the magnitude of these forces as a function of the position of the pumping unit mechanism, specifically the ratio of the angles of the main beam 138 to the crank arm 134 as determined by the equation in figure 3, resulting in a torque signature of the composite engine that is difficult to decipher, specifically difficult to correlate with a specific position. The dynamic forces of the pumping rod and complex pumping unit geometries further confuse the motor torque signature.
    [048] The load torque observed on engine 130 is also affected by the following variable influences:
    [049]. fluid level [050]. pump filling [051]. pumping speed [052]. control mode (speed profiling, dual speed, rod load control, etc.).
    [053] Fluid gas content [054] Other
    Petition 870180011356, of 02/09/2018, p. 18/33
    14/21 [055] The highly variable load torque resulting from stem 148, pump 110, fluid, dynamics, etc., are decoupled from the motor 130 at the two mechanism pivot points, making it possible to interpret the torque at these points, finally allowing the position of the crank arm 134 to be identified. Three torque effects persist at the points of articulation, however, which must be identified. Torque effects include: rotary inertia effects, gearbox friction, and some counterbalance effect. The counterweight torque effect (at the pivot points) results from an asynchronous relationship between the rotating counterweight (which behaves like a sinusoidal torque) and the pumping unit crank “torque factor” (which behaves like distorted sinusoidal). The distortion in the crank “torque factor” is caused by the pumping unit crank pivot being displaced from the steering lever pivot 136, as well as the pivot movement of the main beam 138, both of which create an asymmetry between the crank arm 134 and the counterweight effect. The pumping unit behaves like a “four-bar connection,” (see figure 2) whereas the counterweight behaves like a pure sinusoidal. These differences in behavior create a slight asymmetry at the points of articulation, as well as what is referred to as a counterweight “phase angle” in the technique. Consequently, the two mechanism pivot points do not occur exactly at 0 and 180 degrees of the crank, nor are they all separated at exactly 180 degrees, resulting in some moment of rotary counterbalance at the points of articulation (since the rotating counterweights exert a purely torque) sinusoidal as they rotate around the crank arm). The invention takes advantage of the difference between the sinusoidal, symmetrical counterweight versus the non-symmetrical nature of the pivot point in the mechanism - allows pivot points to be identified.
    [056] At the articulation points, the load observed by engine 130 is comprised of Petition 870180011356, of 02/09/2018, p. 19/33
    15/21 of rotating inertia only, moment of counterbalance and rotating friction. The counterbalance moment at each point of articulation is typically a unique, different value. The points of articulation are asymmetrical and therefore identifiable. The invention's algorithm takes advantage of the fact that the counterbalance moment is a unique value at each point of articulation, and that the points of articulation are asymmetrical and separated at a known distance. This disclosure uses the fact that the effects of rotary inertia can be calculated (since they are predictable) or can be automatically identified in the above-mentioned established ID Well routine revealed in USPN 7,168,924 to characterize the pumping unit system. This disclosure configures the controller to identify the unique torque signature associated with the pivot points, thereby allowing the position of the crank arm 134 to be identified during normal operation (also referred to as production pumping) of the pumping system 104.
    [057] To identify the unique torque signature mentioned above, controller 124 must first decouple the effects of rotary inertia and rotary friction from the crank torque (crank torque is motor torque times gear ratio times gear efficiency). gear). The resulting value is referred to as the “rxless torque,” and comprises only load torque and counterbalance torque. Rotating inertia and rotating frictional effects were decoupled. If these influences did not decouple, the articulation torque levels would be subject to changes in pumping speed. With the effects decoupled, the rxless articulation torque levels are insensitive to changes in speed, allowing the 104 system to operate at various speeds.
    [058] During the initial incorporation of the pumping system, the preferred embodiment of the invention uses an identification routine to store the “rxless torque” value at each of the pivot points. An inclinometer (or other device) 870180011356, from 02/09/2018, page 20/33
    16/21 position reference device) is attached to the pumping unit at the moment. The positions of the crank pivot point are pre-calculated based on the geometry of the pumping unit. As such, the system can “learn” rxless torque levels at the pivot points (while the pumping unit is operating in a calibration mode). In addition, the preferred mode of disclosure also locks (stores) the derivative of the rxless torque, providing yet another feature of each pivot point (either increasing or decreasing the rxlss monitor as the crank passes through the pivot point). This additional feature (known as the “rule” RISE or FALL) will narrow the potential for a mismatch during normal operation (production) of the system, making it even more robust (see figure 9). The initial incorporation is then completed, and the temporary inclinometer can be removed.
    [059] Subsequently, during normal operation (production) of pump 110, the “rxless torque” is continuously sampled, together with the relative position of the crank arm 134. The system compares the rxless torque value with the value of torque value. “learned” (stored) rxless torque (locked during incorporation) for the best match, looking for two rxless torque values that match the known locked rxless values (at pivot points) spaced by the known crank arm distance, 134, between points articulation, and also obeying the RISE or FALL rule of the rxless torque derivative. When a match is found, the relative crank position can subsequently be referenced (corrected) with the position associated with the marriage, thereby referring absolutely to the position of the crank arm 134. This part can be thought of as a pattern recognition. The crank reference is now complete, and the system will be able to plot dynamometer graphs and control the pumping system in production pumping, therefore in combination with the system disclosed in US patent 7,168,924.
    Petition 870180011356, of 02/09/2018, p. 21/33
    17/21 [060] Figure 4 is a flow chart representative of the initial incorporation process. Each step is performed by computer 126 on controller 124.
    [061] 1. The crank angle positions of the pivot point of the unit and pumping of the upstroke and downstroke are determined from the geometry of the pumping unit, illustrated in figure 2. This is done on the controller computer by processing the equation in figure 3 to find the Crank Arm angles where the upper Life angle is both maximized and minimized, corresponding to the upward and downward travel point pivot angle positions, respectively.
    [062] 2. The crank angle distance between the pivot point positions identified in step 1 is computed.
    [063] 3. A temporary inclinometer device is attached to the upper beam of the pumping unit.
    [064] 4. The crank torque is determined from the engine torque in accordance with US patent no. 7,168,924. Crank torque is equal to the engine torque divided by the gear ratio between the engine and crank.
    [065] 5. While the pumping unit is operating, the crank speed is derived from the engine speed as described in US patent no. 7,168,924. The crank speed is equal to the engine speed divided by the gear ratio between the engine and the crank.
    [066] 6. The crank acceleration is determined by differentiating the crank speed.
    [067] 7. The controller identifies the total rotary inertia (on the crank) by accelerating the pumping unit crank through one of the mechanism pivot points at two different acceleration rates while locking (storing) the resulting crank torque values precisely as the mechanism passes through the pivot point. The rotary inertia can be subsequently petition 870180011356, of 02/09/2018, p. 22/33
    18/21 solved by applying the following equation:
    [068] rotary lnteria = (torque-torque2) / (accel ratei - accel rate2) [069] 8. A normalized torque value is derived by subtracting the rotating inertia multiplied by the crank torque.
    [070] 9. The value of “torque rxless” is generated by subtracting a friction term from inertially normalized torque. The friction term is a constant preset value (Coulomb friction) plus a preset gain times the crank speed (viscous friction). An example rxless torque signal is shown in figure 8 along with a dash illustrating an upward stroke versus a downward stroke status. The x and y coordinate units are not relevant.
    [071] 10. The crank angle is monitored as described in US patent 7,168,924, and the rxless torque value is locked and stored at the precise moment when the crank angle passes through the articulation angles calculated in step 1, thereby resulting in the stored up and down travel pivot point torque values.
    [072] 11. The temporary inclinometer is removed from the pumping unit as it is no longer needed. Initial incorporation is completed.
    [073] Figure 5 is a flowchart representative of the normal operating mode (production pumping) of the pumping system (how the pumping system produces fluids to the surface during normal operation). Each step is performed on computer 126 at controller 124.
    [074] A. the crank torque value is determined from the engine torque according to US patent 7,168,924.
    [075] B. motor speed is derived from motor speed as described in US patent 7,168,924. The crank speed is equal to the engine speed divided by the gear ratio between the engine and the crank. The gear ratio is determined by the user.
    Petition 870180011356, of 02/09/2018, p. 23/33
    19/21 [076] C. the crank acceleration is determined by differentiating the crank speed.
    [077] D. a normalized torque signal is derived by subtracting the rotating inertia multiplied by the crank torque.
    [078] E. the “rxless torque” signal is generated by subtracting a friction term from the inertially normalized torque. The friction term is a constant preset value (Coulomb friction) plus a preset gain times the crank speed (viscous friction). An example rxless torque value is shown in figure 8 along with a dash illustrating an upstroke versus a downstroke status. The x and y coordinate units are not relevant.
    [079] F. the relative crank position is determined from the engine position in accordance with US patent 7,168,924. The relative crank position represents the position of the crank, but its absolute position is unknown. Consequently, as the crank rotates, the relative crank position follows, but is shifted from the effective crank position. The displacement is unknown at that time.
    [080] G. the rxless torque value is monitored as the pumping unit is operating. If the rxless torque value is comprised within a stored (locked) upstream stroke torque tolerance, then continue:
    [081] H. if the sign of the derivative of the same rxless signal matches the sign of the stored upward stroke articulation point rule (RISE or FALL) (see figure 9), then it is possible that the position corresponding to that point represents the point and articulation ascending course (position of candidate articulation), and therefore continue:
    [082] l. store the current relative crank position in a set [x], and increment x. as such, the controller can store and track various positions of
    Petition 870180011356, of 02/09/2018, p. 24/33
    20/21 joint candidates.
    [083] J. track the relative crank position.
    [084] K. check to see if the relative crank position has increased to a value equal to the calculated crank angle distance between the pivot points for every stored crank position [x]. if so, continue:
    [085] L. the rxless torque value is monitored. If the rxless torque value is within a tolerance of the stored (locked) downward stroke point torque, then continue:
    [086] M. if the sign of the derivative of the same rxless value matches the sign of the stored upward stroke point rule (RISE or FALL), then the position corresponding to that point represents the downward stroke point joint, and therefore the position absolute value of the crank was identified. Continue:
    [087] N. adjust the relative crank position estimate for the downward pivot point crank angle. The crank position is now absolutely referenced. Return to step A and reference the absolute crank position again with each stroke of the pumping unit (since the position may deviate).
    [088] Figure 9 shows how the rxless torque value levels and RISE or FALL rules correspond to the absolute crank position, illustrating how the method can work. Changes in the status of the Pump Direction signal (labeled upward and downward stroke) occur at the pivot points of the pumping unit mechanism. The controller recognizes the two levels at the points of articulation separated by the correct crank angle distance and obeying the rules (RISE or FALL). When the pattern is recognized, the pivot point is identified and the controller references the crank position.
    [089] For the purpose of this disclosure, the term “coupled” means the joining of two components (electrical or mechanical) directly or indirectly to each other. such a junction can
    Petition 870180011356, of 02/09/2018, p. 25/33
    21/21 be stationary or mobile in nature. Such a junction can be achieved with the two components (electrical or mechanical) and any additional intermediate elements being integrally formed as a single unitary body with each other or the two components and any additional element being fixed together. Such a union may be of a permanent nature or alternatively be of a removable or release nature.
    [090] Although the above description of the present mechanism has been shown and described with reference to specific modalities and applications of it, it has been presented for purposes of illustration and description and is not intended to be exhaustive or to limit the disclosure to the specific modalities and applications disclosed. It will be apparent to those of ordinary skill in the art that various changes, modifications, variations or alterations to the mechanism as described here can be made, none of which depart from the spirit or scope of the present disclosure. The specific modalities and applications have been chosen and described to provide the best illustration of the mechanism's principles and its practical application to thereby allow a person with common knowledge of the technique to use disclosure in various modalities and with various modifications as are appropriate for the specific use. considered. All such changes, modifications, variations and alterations are therefore to be viewed as being within the scope of the present disclosure as determined by the appended claims when interpreted according to the extent to which they are reasonably, legally and equitably entitled.
    Petition 870180011356, of 02/09/2018, p. 26/33
    1/4
    权利要求:
    Claims (10)
    [1]
    1. Method for determining the position of a pumping rod pumping system (104) without a position detector device during production pumping, the pumping system including a rod column (144) carrying a downhole pump ( 110), a variable drive coupled to the stem column (144) for reciprocating movement of the stem column (144) in a well bore (112) and for pump operation, and a crank arm (134) with a counterweight (142) coupled to a main beam (138) with a steering lever (136) and motor (130), with the motor coupled to a controller (122), the method CHARACTERIZED because it comprises:
    - performing an initial incorporation procedure to determine (8, 9) a rxless torque signal at points of articulation of the crank arm (134) during a non-production pumping cycle;
    - measure (D, Ε) the rxless torque signal;
    - store the rxless torque signal in a steel bench coupled to the controller (122);
    - continuously sample the rxless torque;
    - determine (F) the position of the crank arm (134) in relation to the sampled rxless torque;
    - compare, (G, H, L, M) with the controller (122), the rxless torque sampled with the stored rxless torque signal;
    - determine two of the sampled rxless torque signals that correspond to the stored rxless torque signals spaced by the crank arm articulation points (134); and
    - adjust, with the controller (122), the pumping system for optimal operation of the pumping system without a crank arm position sensor (134) during pumping production by identifying a pivot pointPetition 870180011356, from 02/09 / 2018, p. 27/33
    [2]
    2/4 tion and adjust (I, N) the crank arm position estimation signal (134) equal to the value corresponding to the crank position at that point of articulation.
    2. Method for determining the position of a pumping rod pumping system (104) without a position detection device during production pumping, according to claim 1, CHARACTERIZED by the fact that it further comprises: defining a articulation as one of an upper dead center and lower neutral position of the main beam (138) when the rod column (144) is, respectively, in a maximum and minimum extended position.
    [3]
    3. Method for determining the position of a pumping rod pumping system (104) without a position detection device during production pumping, according to claim 2, CHARACTERIZED by the fact that the relationship between the counterweight (142 ) of the crank arm (134) and the steering lever pivot (136) is asymmetrical.
    [4]
    4. Method for determining the position of a pumping rod pumping system (104) without a position detection device during production pumping, according to claim 2, CHARACTERIZED by the fact that it comprises the pivot point is a a descending course and an ascending course.
    [5]
    5. Method for determining the position of a pumping rod pumping system (104) without a position detection device during production pumping, according to claim 1, CHARACTERIZED by the fact that it further comprises: determining (10) the rxless torque derivative and store the derivative in the database, with an rxless torque derivative associated with each pivot point.
    [6]
    6. Pump control system to control the performance of a pumping rod pumping system (104) during product pumping. 870180011356, from 02/09/2018, p. 28/33
    3/4 tion of a well, the pumping rod pumping system including a rod column (144) carrying a downhole pump (110), a variable drive coupled to the rod column (144) for reciprocating movement of the stem column (144) in a well bore (112) and operating the pump, and a crank arm (134) with a counterweight (142) coupled to a main beam (138) with a steering lever (136), the pump control system CHARACTERIZED by the fact that it comprises:
    - controller (122) coupled to a database (128), with controller (122) configured to access an rxless torque in the database, with the stored rxless torque representative of crank arm articulation points (134) during an initial calibration pumping cycle, the controller (122) additionally configured to continuously sample the system's rxless torque and determine the position of the crank arm (134) in relation to the sampled rxless torque; and
    - motor (130) coupled to the steering lever (136) and crank arm (134), with the performance of the motor controlled by the controller (122) based on a comparison (G, L) by the controller of the rxless torque value sampled with the stored rxless torque value, an identification of two of the sampled rxless torque values that correspond to the stored rxless torque value spaced by the crank arm pivot points (134), and an adjustment of the motor position estimate by the controller ( 122) to adjust the crank arm position (134) to a pivot point for optimal operation of the pumping system (104) without a crank arm position sensor (134) during production pumping.
    [7]
    7. Pump control system to control the performance of a pumping rod pumping system (104) during pumping production from a well, according to claim 6, CHARACTERIZED by the fact that
    Petition 870180011356, of 02/09/2018, p. 29/33
    4/4 which further comprises configuring the controller (122) to define a pivot point as one of an upper dead center and lower neutral position of the main beam (138) when the stem column (144) is, respectively, in a maximum and minimum extended position.
    [8]
    8. Pump control system to control the performance of a pumping rod pumping system (104) during pumping production from a well, according to claim 7, CHARACTERIZED by the fact that the relationship between the counterweight (142 ) of the crank arm (134) and the steering lever pivot (136) is asymmetrical.
    [9]
    9. Pump control system to control the performance of a pumping rod pumping system (104) during pumping production from a well, according to claim 7, CHARACTERIZED by the fact that the pivot point is one of a descending course and an ascending course.
    [10]
    10. Pump control system to control the performance of a pumping rod pumping system (104) during pumping production from a well, according to claim 6, CHARACTERIZED by the fact that it comprises the configured controller (122) to determine (10) the rxless torque derivative and store the derivative in the database, with an rxless torque derivative associated with each pivot point.
    Petition 870180011356, of 02/09/2018, p. 30/33
    1/8
    2/8
    R 5 sin
    Rj si π (Ψ | - Φθ)
    R 6 -ψοϊ ^ -Φθ) + (ZRjRgCOSWj-.ígl + Rg + Rg - R, 2 - R g 2 ΜΊ
    COS tan 1 <
    2R 5 R 3 R 3 ” R 5 / 2R 1 R 6 cost * 1 - * 6 ) + R 5 2 + R3 2 -R1 2 -R 6 2 λ> -φ £
    2R 5 R 3
    类似技术:
    公开号 | 公开日 | 专利标题
    BR112015010330B1|2018-04-03|&#34;Method for determining the position of a pumping rod pumping system and pump control system&#34;
    RU2381384C1|2010-02-10|Method and system to control rod travel in system pumping fluid out of well
    US7168924B2|2007-01-30|Rod pump control system including parameter estimator
    CA2936398C|2018-09-18|Diagnostics of downhole dynamometer data for control and troubleshooting of reciprocating rod lift systems
    EA024649B1|2016-10-31|Estimating fluid levels in a progressing cavity pump system
    GB2427661A|2007-01-03|Method for estimating pump efficiency
    US20180128264A1|2018-05-10|Apparatus and methods for counterbalancing a pumping unit
    US10955825B2|2021-03-23|Beam pumping unit and method of operation
    US20140088875A1|2014-03-27|Pumpjack torque fill estimation
    Feng et al.2020|Variable speed drive optimization model and analysis of comprehensive performance of beam pumping unit
    Lindh et al.2015|Generating surface dynamometer cards for a sucker-rod pump by using frequency converter estimates and a process identification run
    US10227970B2|2019-03-12|Determining pump-out flow rate
    US10781813B2|2020-09-22|Controller for a rod pumping unit and method of operation
    Li et al.2019|Practical Parameter Estimator for Dynamometer Card of Rod Pumping Systems by Measuring Terminal Data of Drive Motor
    RU2686787C1|2019-04-30|Method to determine degree of mechanism balance and optimum position of counterweight of sucker rod pumping units
    US10851774B2|2020-12-01|Controller and method of controlling a rod pumping unit
    McCoy et al.1997|Motor power/current measurement for improving rod pump efficiencies
    BR112019010541A2|2019-09-17|system for optimizing the operation of a submersible electric pump motor, computer readable medium, submersible electric pump motor and variable speed drive, and computer-implemented energy optimization method for a submersible electric motor.
    Koncz et al.2018|NEW METHOD FOR STRIPPER WELL SUPERVISION
    Shan et al.2010|Notice of Retraction: Production calculation of oil wells based on Dynamometer Card
    Koncz2015|Innovative Developments in sucker rod pumped well analysis
    Tecle et al.2021|Development of Fault Diagnosis Model for Sucker Rod Pump Using Motor Power Curve
    Silva et al.2014|Determining the surface dynamometer card of a pumping system from the torque curve of a three-phase induction motor
    Lindh et al.0|Creation of Surface Dynamometer Cards of Sucker Rod Pump Using Frequency Converter Estimates and Process Identification Run
    同族专利:
    公开号 | 公开日
    AU2013341473A1|2015-05-21|
    EP2917472A1|2015-09-16|
    US20140129037A1|2014-05-08|
    CA2890587A1|2014-05-15|
    EP2917472A4|2016-07-13|
    EP2917472B1|2017-07-05|
    CA2890587C|2019-01-29|
    EA201500517A1|2015-11-30|
    MX358225B|2018-08-10|
    MX2015005641A|2016-06-29|
    BR112015010330A2|2016-12-06|
    US9353617B2|2016-05-31|
    WO2014074434A1|2014-05-15|
    AR093385A1|2015-06-03|
    AU2013341473B2|2016-11-03|
    EA029265B1|2018-02-28|
    CO7380744A2|2015-09-10|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US4541274A|1984-05-10|1985-09-17|Board Of Regents For The University Of Oklahoma|Apparatus and method for monitoring and controlling a pump system for a well|
    US5204595A|1989-01-17|1993-04-20|Magnetek, Inc.|Method and apparatus for controlling a walking beam pump|
    US6343656B1|2000-03-23|2002-02-05|Intevep, S.A.|System and method for optimizing production from a rod-pumping system|
    US20040062658A1|2002-09-27|2004-04-01|Beck Thomas L.|Control system for progressing cavity pumps|
    US6890156B2|2002-11-01|2005-05-10|Polyphase Engineered Controls|Reciprocating pump control system|
    WO2006034197A2|2004-09-17|2006-03-30|Lufkin Industries, Inc.|Method for mitigating rod float in rod pumped wells|
    US7500390B2|2005-06-29|2009-03-10|Weatherford/Lamb, Inc.|Method for estimating pump efficiency|
    RU2381384C1|2005-10-13|2010-02-10|Пампвелл Солюшнз Лтд.|Method and system to control rod travel in system pumping fluid out of well|
    US7321211B2|2006-04-28|2008-01-22|Unico, Inc.|Power variation control system for cyclic loads|
    US9234517B2|2009-10-26|2016-01-12|Harold Wells Associates, Inc.|Pump control device, oil well with device and method|
    CN201835794U|2010-03-31|2011-05-18|中国石油大学|Drainage and gas production simulation experiment device|
    US8240221B2|2010-08-09|2012-08-14|Lufkin Industries, Inc.|Beam pumping unit for inclined wellhead|
    US20140088875A1|2011-05-06|2014-03-27|Schneider Electric USA, Inc.|Pumpjack torque fill estimation|
    US9041332B2|2011-08-31|2015-05-26|Long Meadow Technologies, Llc|System, method and apparatus for computing, monitoring, measuring, optimizing and allocating power and energy for a rod pumping system|
    US8944157B2|2012-07-11|2015-02-03|Jacob MAIL|Hydro pneumatic lifting system and method|US10094371B2|2014-07-01|2018-10-09|Bristol, Inc.|Methods and apparatus to determine operating parameters of a pumping unit for use with wells|
    US10408206B2|2014-07-01|2019-09-10|Bristol, Inc.|Methods and apparatus to determine parameters of a pumping unit for use with wells|
    CN104481499B|2014-09-11|2017-02-15|哈尔滨斯特凯峰电子有限公司|Electrical parameter based rod pumped well daily fluid production capacity measuring method|
    US10145230B2|2014-10-10|2018-12-04|Henry Research And Development, Llc|Systems and methods for real-time monitoring of downhole pump conditions|
    US10428627B2|2015-09-11|2019-10-01|Encline Artificial Lift Technologies LLC|Controlled pneumatic well pumping system, and method for optimizing pump stroke speed|
    US20160265321A1|2015-03-11|2016-09-15|Encline Artificial Lift Technologies LLC|Well Pumping System Having Pump Speed Optimization|
    CN104818975B|2015-03-16|2018-03-20|浙江理工大学|The glutinous draw-out device of one kind drop|
    CN104775793A|2015-03-16|2015-07-15|浙江理工大学|Oil extracting device|
    CN104818966A|2015-03-16|2015-08-05|浙江理工大学|Recovery well|
    CN104913880B|2015-06-02|2017-09-01|中国石油天然气股份有限公司|A kind of bridge-type concentric roater regulator device for detecting performance|
    US10100623B2|2015-06-30|2018-10-16|KLD Energy Nano-Grid Systems, Inc.|Intra-stroke cycle timing for pumpjack fluid pumping|
    US20170002805A1|2015-06-30|2017-01-05|KLD Energy Nano-Grind Systems, Inc.|Electric motor control for pumpjack pumping|
    US11028844B2|2015-11-18|2021-06-08|Ravdos Holdings Inc.|Controller and method of controlling a rod pumping unit|
    CN105298469A|2015-10-20|2016-02-03|北京恒和兴业科技发展有限公司|Monitoring system and monitoring method for running state of beam-pumping unit|
    US10408205B2|2016-08-04|2019-09-10|Schneider Electric Systems Canada Inc.|Method of determining pump fill and adjusting speed of a rod pumping system|
    US10340755B1|2016-11-14|2019-07-02|George R Dreher|Energy harvesting and converting beam pumping unit|
    US10669787B2|2016-12-09|2020-06-02|Schlumberger Technology Corporation|Pump rod connection|
    CN108979623A|2018-06-20|2018-12-11|陕西安控科技有限公司|A kind of recognition methods of exception indicator card|
    CN109063629A|2018-07-27|2018-12-21|滕奇刚|A method of pumping unit lower dead point position on identification oil pumping electromechanical parameters curve|
    US11240426B2|2019-06-20|2022-02-01|Cilag Gmbh International|Pulsed illumination in a hyperspectral, fluorescence, and laser mapping imaging system|
    CN110346082B|2019-07-18|2021-03-09|青岛江林驱动科技有限公司|Calibration method of beam-pumping unit suspension point stress measurement system|
    EP3816444A1|2019-10-30|2021-05-05|Siemens Energy Austria GmbH|Method for determining operating properties of a rod borehole pump and pump system for same|
    RU2724712C1|2019-11-29|2020-06-25|Публичное акционерное общество «Татнефть» имени В.Д. Шашина|Installation for simultaneous separate extraction and injection|
    法律状态:
    2017-11-14| B06A| Notification to applicant to reply to the report for non-patentability or inadequacy of the application [chapter 6.1 patent gazette]|
    2018-02-27| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2018-04-03| B16A| Patent or certificate of addition of invention granted|
    2020-02-18| B25D| Requested change of name of applicant approved|
    优先权:
    申请号 | 申请日 | 专利标题
    US201261722884P| true| 2012-11-06|2012-11-06|
    US61/722.884|2012-11-06|
    US13/960,903|US9353617B2|2012-11-06|2013-08-07|Apparatus and method of referencing a sucker rod pump|
    US13/960.903|2013-08-07|
    PCT/US2013/068229|WO2014074434A1|2012-11-06|2013-11-04|Apparatus and method of referencing a sucker rod pump|
    [返回顶部]