Patent Application
20140129037
The present disclosure relates generally to control of sucker rod pumps for oil, gas, and water wells, and move particularly to an apparatus and methods to determine position of a sucker rod pumping system without a position sensing device during production pumping for optimizing the operation of the rod pump.
A sucker rod pumping unit reciprocates a rod string to actuate a subterranean pump for the purpose of lifting liquids to the surface. An exemplary embodiment is shown in
In addition to tracking system performance, these sensors can also be used to improve or optimize the pumping system operation, maximize production rates, and/or protect pumping equipment. For example, feedback information from sensors allows for the generation of “dynamometer plots” (pump load versus position data) which can be used to infer valuable down-hole conditions such as pump load, pump flow rate, well inflow, and pump health, which can in turn be used to improve or optimize the pumping system operation.
Sensors externally affixed to a pumping unit add additional cost, represent a potential failure mode, require frequent maintenance, and are often not functional owing to poor maintenance or neglect. Failure of these devices, especially in remotely located areas, can cause the pumping system to operate to sub-optimally, possibly hindering production rates and/or causing damage to the pumping system.
U.S. Pat. No. 7,168,924 describes a method whereby the rod load cell sensor may be eliminated, thus providing a less expensive and more reliable system. The '924 patent is assigned to the assignee of this application and is incorporated herein, in full, as if fully set-forth herein. However, a positioning sensor of some kind is still required for referencing of the absolute position of the pumping unit. This could include a crank position sensor (a discretely activated sensor or switch affixed to the pumping unit crank arm), an inclinometer affixed to the pumping unit main beam (Also referred to as a walking beam), or any other such method of determining crank position with an externally mounted “reference” device.
The apparatus of the present disclosure must also be of construction which is both durable and long lasting, and it should also require little or no maintenance to be provided by the user throughout its operating lifetime. In order to enhance the market appeal of the apparatus of the present disclosure, it should also be of inexpensive construction to thereby afford it the broadest possible market. Finally, it is also an objective that all of the aforesaid advantages and objectives be achieved without incurring any substantial relative disadvantage.
The disadvantages and limitations of the background art discussed above are overcome by the present disclosure.
There is provided a method and system to determine the position of a sucker rod pumping system without a position sensing device during production pumping. The pumping system includes a rod string carrying a downhole pump, a variable drive coupled to the rod string for reciprocation of the rod string within a wellbore and operating the pump. A crank arm, with a counter weight, is coupled to a main beam with a pitman arm and motor. The motor is coupled to a controller.
The method includes performing an initial commissioning procedure to determine an rxless torque value at toggle points of the crank arm during an initial calibration pumping cycle. The rxless torque value is measured and stored in a database coupled to the controller. During normal production pumping operation the controller continuously samples the rxless torque and determines the crank arm position in relation to the sample rxless torque value. The controller compares the sample rxless torque value to the stored rxless torque value and determines two of the sampled rxless torque values that correspond to the stored rxless torque values by the crank arm toggle points.
The controller adjusts the pumping system for optimal operation of the pumping system without a crank arm position sensor during production pumping by identifying a toggle point and setting the crank arm position estimate equal to the value corresponding to the crank position at that toggle point.
In one embodiment, the method includes defining a toggle point as one of a top dead center and bottom dead center position of the main beam when the rod string is at, respectively, a maximum and minimum extended position. In another embodiment, the method includes determining the rxless torque derivative and storing the derivative in the database. Each toggle point has an rxless torque derivative associated with it.
There is further provided a pump control system for controlling the performance of a sucker rod pump system during production pumping of a well. The sucker rod pumping system includes a rod string carrying a downhole pump, a variable drive coupled to the rod string for reciprocation of the rod string within a wellbore and operating the pump. A crank arm, with a counter weight, is coupled to a main beam with a pitman arm.
A pump control system of the sucker rod pumping system includes a controller coupled to a database, with the controller configured to access an rxless torque value in the database. With the stored rxless torque value representative of toggle points of the crank arm during an initial calibration pumping cycle, the controller further is configured to continuously sample the rxless torque value of the system and determine the crank arm position in relation to the sample rxless torque value. The system also includes a motor coupled to the pitman arm and the crank arm, with the performance of the motor controlled by the controller based on a comparison, by the controller, of the sampled rxless torque value to the stored rxless torque value. An identification is made of two of the sampled rxless torque values that correspond to the stored rxless torque values spaced by the crank arm toggle points. The controller then adjusts the motor, speed or torque by the controller to set the crank arm position to a toggle point for optimal operation of the pumping system without a crank arm position sensor during production pumping. In another embodiment, the pump control system includes configuring the controller to define a toggle point as one of a top dead center and bottom dead center position of the main beam when the rod string is at, respectively, a maximum and minimum extended position. In a further embodiment, the pump control system is configured such that the relationship between the crank arm counter weight and the pitman arm pivot is asymmetric.
The apparatus of the present invention is of a construction which is both durable and long lasting, and which will require little or no maintenance to be provided by the user throughout its operating lifetime. Finally, all of the aforesaid advantages and objectives are achieved without incurring any substantial relative disadvantage.
These and other advantages of the present disclosure are best understood with reference to the drawings, in which:
5
Sucker rod pumping units are typically driven by an electric motor as the prime mover. In accord with the present disclosure a user is able to determine the crank position of the pumping unit (and therefore the absolute position reference) directly from the prime-mover motor torque and speed (derived from motor current and voltage). Once the absolute position of the crank and main beam are determined, the position of the sucker rod may be subsequently determined using information about the specific pump unit (as described below), where rod position is proportional to the main beam angle times the total rod stroke.
The preferred embodiment uses a system identification routine during initial calibration (also referred to as commissioning) for identifying the rotary inertia of the system, comprising the crank arm, gearbox, sheaves, and prime-mover motor armature. This routine is initially executed during pump commissioning with an inclinometer (or some other absolute positioning device) temporarily affixed to the pumping unit. Such commission of the system is done in a calibration pump cycle. The initial calibration procedure identifies and characterizes parameters of the system. During this routine, the pumping unit rotary inertia is characterized, and a normalized upstroke and down-stroke mechanism “toggle point” torques levels are stored, as described below. Alternatively, the rotary inertia could be preset or calculated by some means other than the system identification routine. The inclinometer device is subsequently removed and the system is operated in a production pump cycle without sensors on the pump structure or downhole in the wellbore.
Referring to
The walking beam 138, in turn, is actuated by the pitman arm 31 which is reciprocated by a crank arm 134 driven by an electric motor 130 that is coupled to the crank arm 134 through a gear reduction mechanism, such as gearbox 132. The typical motor 130 can be a three-phase AC induction motor operable at 460 VAC and developing 10 125 horsepower, depending upon the capacity and depth of the pump. Other types of motors such as synchronous motors can be used to drive the pumping unit. The gearbox 132 converts motor torque to a low speed but high torque output for driving the crank arm 134. The crank arm 134 is provided with a counterweight 142 that serves to balance the rod string 144 suspended from the beam 138 in the manner known in the art. Counterbalance can also be provided by an air cylinder such as those found on air-balanced units. Belted pumping units may use a counterweight that runs in the opposite direction of the rod stroke.
The downhole pump 110 is a reciprocating type pump having a plunger 116 attached to the end of the rod string 144 and a pump barrel 114 which is attached to the end of tubing in the well 100. The plunger 116 includes a traveling valve 118 and a standing valve 120 positioned at the bottom of the barrel 114. On the up stroke of the pump, the traveling valve 118 closes and lifts fluid, such as oil and/or water, above the plunger 116 to the top of the well and the standing valve 120 opens and allows additional fluid from the reservoir to flow into the pump barrel 114. On the down stroke, the traveling valve 118 opens and the standing valve 120 closes in preparation of the next cycle. The operation of the pump 100 is controlled so that the fluid level maintained in the pump barrel 114 is sufficient to maintain the lower end of the rod string 144 in the fluid over its entire stroke.
In one embodiment, instantaneous motor currents and voltages together with pump parameters are used in determining rod position and load without the need for strain gauges, load cells, or position sensors as well as determining pump pressure and pump flow without the need for additional downhole or surface sensors. The rod position and load can be used to control the operation of the pump 110 to optimize the operation of the pump 110. In addition, American Petroleum Institute (API) specifications have been used to define the pump geometry that allows the use of readily available data from pump manufacturers. System identification routines are used to establish installation dependent parameters specific to the particular pump used in calculating performance parameters that are used in real-time closed loop control of the operation of the rod pump, obviating the need to create large look-up tables for parameter values used in calculating performance parameters.
The pump control system 104 includes transducers, such as current and voltage sensors, to sense dynamic variables associated with motor torque and velocity. Current sensors are coupled to a sufficient number of the motor leads for the type of motor used. The current sensors provide voltages proportional to the instantaneous stator currents in the motor 130. Voltage sensors are connected across to a sufficient number of the motor windings for the type of motor used and provide voltages proportional to the instantaneous voltages across the motor windings. The current and voltage signals produced by sensors are supplied to a processor 124 through suitable input/output devices. The processor 124 further includes a processing unit 126 and storage devices 128 which stores programs and data files used in calculating operating parameters and producing control signals for controlling the operation of the rod pump system 104. This control arrangement provides nearly instantaneous readings of motor velocity and torque which can be used for both monitoring and real-time, closed-loop control of the rod pump. For example, in one embodiment, computations of motor velocity and torque used for real-time, closed-loop control are provided at the rate of 1000 times per second.
Motor currents and voltages are sensed to determine the instantaneous electric power level drawn from the power source by the electric motor operating the well pump. As the rod string 144 that drives the downhole pump 110 is raised and lowered during each cycle, the motor 130 is cyclically loaded. Depending on the particular pump installation configuration, the walking beam 139 is at a known position during maximum and minimum motor loads. The timing of these maximums and minimums can define the operational pumping frequency and, by integration of the motor velocity in light of the motor to crank gearing, it is possible to estimate the phase position of the pump crank at any time. By monitoring the variances of the motor currents and voltages as a function of pump crank angle, the voltage and current variances can be used together with parameters related to pump geometry to calculate estimates of rod position and rod load.
The apparatus and method described herein applies to the control of traditional sucker rod “pump jacks” with “crank arm” counterbalance mechanism as shown in
This disclosure allows a sucker rod pump controller 124 to generate “dynamometer plots,” as shown in
The controller 124 must generate a value representative of the pumping unit position, such as the angle of the crank arm 134. According to the disclosure, the angle of the crank arm can be periodically determined by analysis of the motor torque coupled with knowledge of the pumping unit geometry, specifically the pumping unit “toggle points.” The toggle points are defined as “top dead center” and “bottom dead center” positions of the pumping unit 104 main beam 138, where the rod is at its maximum and minimum extended positions, as the “torque factor” (as known in the art) passes through zero.
The toggle points represent unique singularities during the polished rod 146 stroke, providing small “windows” which the controller 124 can use to identify the crank arm 134 position from the crank torque value. As the pumping unit passes through its toggle points, the crank torque (and therefore motor torque) is completely decoupled from complex effects of the rod load. At the toggle points, the motor torque is influenced solely by the effects of motor 130 and pumping unit rotary inertia, pumping unit counterweight effect, and rotary friction, all of which can be adequately estimated and therefore predicted or measured upon initial commissioning. Furthermore, these “windows” occur at regular intervals, and the relative distance between said intervals can be analytically predetermined given the geometry of the pumping unit.
During portions of the pumping unit cycle other than its toggle points, the motor torque is influenced by several confounding factors. If one were to attempt to determine the crank position (reference the pumping unit) based on analysis of the motor torque during any portion of the cycle other than the toggle points, the complexity of the aforementioned influences would render the technique untenable. As such, it is extremely difficult to correlate the motor torque to motor position at any point during the cycle other than the unit toggle points (where the expected torque is more highly predictable).
Expounding upon this point, following is a list of the various forces that contribute to the torque observed at the prime mover motor 130, comprising:
30
The various forces listed above are translated back to the motor 130, as a torque, through the geometry of the pumping unit. The geometry of the pumping unit mechanism (See
The load torque observed at the motor 130 is also affected by the following variable influences:
The highly variable load torque resulting from the rod 146, pump 110, fluid, dynamics, etc. are decoupled from the motor 130 at the two mechanism toggle points, making interpretation of the torque at those points possible, ultimately allowing the crank arm 134 position to be identified. Three torque effects persist at the toggle points, however, which must be identified. Said torque effects include: rotary inertia effects, gearbox friction, and some counterweight effect. The counterweight torque effect (at the toggle points) results from an asynchronous relation between the rotary counterweight (which behaves as a sinusoidal torque) and the pumping unit crank “torque factor” (which behaves as a distorted sinusoid). The distortion in the crank “torque factor” is caused by the pumping unit crank pivot being offset from pitman arm 136 pivot, as well as the pivoting motion 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 linkage,” (See
At the toggle points, the load observed by the motor 130 is comprised solely of rotary inertia, counterbalance moment, and rotary friction. The counterbalance moment at each toggle point is typically a different, unique value. The toggle points are asymmetrical, and therefore identifiable. The invention algorithm takes advantage of the fact that the counterbalance moment is a unique value at each toggle point, and that the toggle points are asymmetrical and a known distance apart. This disclosure utilizes the fact that the rotary inertia effects can be either calculated (since they are predictable) or can be automatically identified in the aforementioned established Well ID routine disclosed in the U.S. Pat. No. 7,168,924 to characterize the pumping unit system. This disclosure configures the controller to identify the unique torque signature associated with the toggle points, thereby allowing the crank arm 134 position to be identified during the normal (also referred to as production pumping) operation of the pumping system 104.
To identify the aforementioned unique torque signature, the controller 124 must first decouple the effects of the rotary inertia and rotary friction from the crank torque (crank torque is motor torque times gear ratio times gearbox efficiency). The resulting value is referred to as the “rxless torque,” and comprises only load torque and counterbalance torque. Rotary inertia and rotary frictional effects have been decoupled. Were these influences not decoupled, the toggle torque levels would be subject to changes in pumping speed. With the effects decoupled, the rxless toggle torque levels are insensitive to speed changes, allowing the system 104 to function over various speeds.
During the initial commissioning of the pumping system, the preferred embodiment of the invention uses an identification routine to store the “rxless torque” value at each the toggle points. An inclinometer (or other position reference device) is affixed to the pumping unit at the time. The toggle point positions of the crank are pre-calculated based upon the geometry of the pumping unit. As such, the system can “learn” the rxless torque levels at the toggle points (while the pumping unit is running in a calibration mode). In addition, the preferred embodiment of the disclosure also latches (stores) the derivative of the rxless torque, providing yet another characteristic of each toggle point (whether increasing or decreasing rxless monitor as the crank passes through the toggle point). This additional characteristic (known as RISE or FALL “rule”) will narrow the potential for an erroneous match during normal (production) operation of the system, making it more robust (See
Subsequently, during the normal (production) operation of the pump 110, the “rxless torque” is continuously sampled, along with the crank arm 134 relative position. The system compares the rxless torque value to the “learned” (stored) rxless torque value data (latched during commissioning) for the best match, looking for two values of rxless torque that equal the known latched rxless values (at the toggle points) spaced by the known crank arm 134 distance between toggle points, and also obeying the RISE or FALL rule of the derivative of rxless torque. When a match is found, relative crank position can subsequently be referenced (corrected) to the position associated with the match, thus absolutely referencing the crank arm 134 position. This part can be thought of as pattern recognition. The crank reference is now complete, and the system will be capable of drawing dynamometer plots and controlling the pumping system in production pumping accordingly in conjunction with the system disclosed in U.S. Pat. No. 7,168,924.
rotary inertia=(torque1−torque2)/(accel rate1−accel rate2)
For purposes of this disclosure, the term “coupled” means the joining of two components (electrical or mechanical) directly or indirectly to one another. Such joining may be stationary in nature or moveable in nature. Such joining may be achieved with the two components (electrical or mechanical) and any additional intermediate members being integrally formed as a single unitary body with one another or the two components and any additional member being attached to one another. Such adjoining may be permanent in nature or alternatively be removable or releasable in nature.
Although the foregoing description of the present mechanism has been shown and described with reference to particular embodiments and applications thereof, it has been presented for purposes of illustration and description and is not intended to be exhaustive or to limit the disclosure to the particular embodiments and applications disclosed. It will be apparent to those having ordinary skill in the art that a number of changes, modifications, variations, or alterations to the mechanism as described herein may be made, none of which depart from the spirit or scope of the present disclosure. The particular embodiments and applications were chosen and described to provide the best illustration of the principles of the mechanism and its practical application to thereby enable one of ordinary skill in the art to utilize the disclosure in various embodiments and with various modifications as are suited to the particular use contemplated. All such changes, modifications, variations, and alterations should therefore be seen as being within the scope of the present disclosure as determined by the appended claims when interpreted in accordance with the breadth to which they are fairly, legally, and equitably entitled.
CROSS-REFERENCE TO RELATED PATENT APPLICATIONS This application is a non-provisional application claiming priority to Provisional Application Ser. No. 61/722,884 filed Nov. 6, 2012, which is incorporated herein, in its entirely, by this reference.
| Number | Date | Country | |
|---|---|---|---|
| 61722884 | Nov 2012 | US |
