2.2. Fault Mechanism Model
- (1)
Current Fault Model
The current method is the quantitative long-time measurement of parameters such as operating current, voltage, and power of the drive motor using specialized instruments. The motor input current is deduced based on the motor output power:
where
I1 is the motor input current, A;
Ne is the power under a rated load, kW;
IN is the stator current of the motor under a rated load, A;
I0 is the no-load current of the motor, A.
N1 is the output shaft power of the motor, kW;
Mg is the driving torque of the rod, N⋅m;
ng is the rotational speed of the rod, r/min; and
ηt is the total transmission efficiency of the motor, %.
After analysis, the relationship between electrical parameters and torque can be obtained as shown below:
The analysis shows that the square of the motor input current is proportional to the square of the rod torque.
According to Equation (2), it can be deduced that when the current drops to the no-load current, which means the rod torque drops to the no-load torque, the oil rod or oil pipe may break off; when the current is smaller than the lower limit of the reasonable range and higher than the lower limit of the limit range, the pump may leak or the oil pipe may leak; when the current fluctuates in the upper limit of the limit range, the oil pipe may be waxed; when the current increases to the outside of the limit range, the stator may be dissolved or the parameters may be high; when the current is smaller than the lower limit of the reasonable range and fluctuates, the stator may be waxed. When the current fluctuates, the stator may be degumming.
- (2)
Load Fault Model
The axial load F on the screw pump rod can be expressed by the following formula:
where
F1 is the rod’s own gravity, N;
F2 is the axial load generated by the pressure difference between the inlet and outlet of the pump, N;
F3 is the friction force between the well fluid and the rod when it flows upward in the pipe, N; and
F4 is the upward buoyancy force that the rod receives in the well fluid, N.
The gravity of the pumping rod can be expressed by the following equation:
where
G is the linear density of the rod, N/m;
L is the total length of the pumping rod, m.
The axial load generated by the pressure difference between the inlet and outlet of the pump can be expressed by the following equation:
where
is the eccentric moment of the screw pump, m;
R is the rotor radius of the screw pump, m;
is the differential pressure between the inlet and outlet of the pump, MPa.
The friction force between the well fluid and the rod can be expressed by the following equation:
where
,
is the length of the section, m;
is the average viscosity of the well fluid, mPa⋅s;
is the average flow speed of the well fluid in the section, m/s.
The buoyancy of the rod generated by well fluid can be expressed by the following equation:
where
is the acceleration of gravity, N/kg;
is the density of the fluid in the wellbore, kg/m
3.
After analyzing, it can be obtained that when decreases, it means the liquid in the screw pump decreases; when increases, it means the oil velocity increases, i.e., the oil production increases. According to Equations (3)–(7), we can conclude that when F is zero, there may be a rod break; when F is reduced, there may be an oil pipe leakage, a broken oil pipe, or pump leakage, etc.; when F is increased, there may be waxing of the oil pipe or high parameters.
- (3)
Rotation Speed Fault Model
The rotate speed of a screw pump is closely related to the oil production, as shown in the following equation:
where
Q is the theoretical oil production, m
3/d;
n is the rotor speed, r/min;
E is the eccentricity of the rotor, m;
D is the truncated circle diameter of the rotor, m;
T is the stator lead, m.
The actual oil production of a screw pump can be expressed by the following equation:
where
is the volumetric efficiency of the screw pump;
is the actual oil production, m
3/d.
It can be seen that after the structural parameters E, D, and T of the screw pump are determined, the oil production is only related to the rotational speed n and the volumetric efficiency , and the rotational speed needs to be increased in order to achieve higher oil production.
Increasing the rotational speed of the screw pump can improve oil production, but extremely high rotational speed will lead to an increase in the centrifugal force of the rod, which will cause vibration and decrease the oil lifting height. At the same time, high speed rotation will also accelerate the wear of stator rubber.
After analyzing, it can be concluded from Equation (9) that when n is zero, the pump may be jammed; when n is reduced, the rod and pipe may show biased wear, or the oil pipe may be waxed, etc.; when n increases, there may be an oil rod break, oil pipe breakage, oil pipe leakage, or pump leakage, and so on.
- (4)
Oil Pressure Fault Model
Letting the oil pressure be
P at the moment of starting pumping
t, the relationship between pressure and volume is:
where
is the compression coefficient of the gas–liquid mixture in the oil pipe;
is the amount of time change, s;
is the amount of pressure change, MPa; and
is the pumping volume flow rate m
3/s.
When pipe leakage occurs, the relationship between the leakage flow rate and the pressure difference between the inside and outside of the oil pipe at the leaking place is:
where
is the leakage flow rate, m
3/s;
ε is the shrinkage coefficient of the leakage section due to the inertia of the liquid;
is the flow coefficient associated with the liquid;
A is the size of the cross-sectional area at the orifice of the liquid leakage, m
2;
g is the acceleration of gravity, m/s
2;
h is the difference in liquid pressure between the inside of the tubing at the location of the leakage and the outside of the tubing, m.
Since the leakage flow rate is a function of pressure P, and increases nonlinearly with P, the relationship between pressure and time is broken when leakage occurs, resulting in a slower rate of pressure increase.