CN110457766A - Measure the method for beam pumping unit suspension point power indirectly based on motor power (output) - Google Patents
Measure the method for beam pumping unit suspension point power indirectly based on motor power (output) Download PDFInfo
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- CN110457766A CN110457766A CN201910648891.4A CN201910648891A CN110457766A CN 110457766 A CN110457766 A CN 110457766A CN 201910648891 A CN201910648891 A CN 201910648891A CN 110457766 A CN110457766 A CN 110457766A
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Abstract
The present invention is based on the methods that motor power (output) measures beam pumping unit suspension point power indirectly, with the crank angle of beam pumping unit, motor power (output) is independent variable, connection and movement relation based on beam pumping unit four-bar mechanism, set up the real-time parameter dynamic model of suspension point, suspension point position can be calculated in real time with the variation of crank angle, the corresponding variation of velocity and acceleration, in addition motor power (output) (P), crank angle (θ) to measure the size of suspension point real-time force indirectly, to effectively improve the real-time and reliability of oil well surveillance, reduce design and production cost.I.e. under the premise of known electric motor power and crank angle, measurement acquires the real-time dynamic stress value of suspension point indirectly.
Description
Technical field
The present invention is a kind of completely new beam pumping unit point suspension movement force measuring method, specifically with crank angle (θ)
It measures the real-time stress value variation for obtaining suspension point indirectly for independent variable with motor power (output) (P), belongs to petrochemical industry oil field and apply
Work production and computer information field.
Background technique
Oil field at home explores construction field at present, more generally uses beam pumping unit.The prior art is transported for suspension point
The solution of dynamic parameter, substantially passes through the change between the polished rod load and stroke of indicator card or electric work figure to disclose motor-pumped well polished rod
Change relationship.
Such as following first open source literature, such as the 107-110 pages of the phase of volume 19 the 2nd of " petroleum journal ", beam pumping unit fortune
The accurate solution of dynamic parameter, 4 monthly magazines in 1998.Walking beam swing equation is established by point suspension movement parameter, to obtain point suspension movement
Displacement, velocity and acceleration calculation formula, finally provide the accurate solution for seeking beam pumping unit point suspension movement parameter.
For another example the 22-24 pages of the phase of volume 34 the 5th of " petroleum machinery ", the many-body dynamics point of motion laws of beam pumping unit
Analysis, 3 monthly magazines in 2006.It is analyzed using many-body dynamics method, with the result of kinetics equation value integral to displacement and speed
Degree grade constraint equation carries out solution and violation model.
The force measuring method that the above-mentioned prior art is realized, calculating process is complicated and has the characteristics that multidimensional, and calculated result is therefore
Also biggish error, the accurate solution in still non-real meaning are just accumulated.In addition, calculating process is excessively complicated and has lower reality
Ground uses reference value.
In view of this, special propose present patent application.
Summary of the invention
The present invention is based on the method that motor power (output) measures beam pumping unit suspension point power indirectly, it is to solve the prior art
There are the problem of and with the crank angle of beam pumping unit (θ), motor power (output) (P) be independent variable, based on beam type pump
The connection and movement relation of machine four-bar mechanism, it is established that the real-time parameter dynamic model of suspension point, i.e., with the variation of crank angle
The corresponding variation of suspension point position, velocity and acceleration can be calculated in real time, in addition motor power (output) (P), crank angle (θ)
To measure the size of suspension point real-time force indirectly, thus effectively improve oil well surveillance real-time and reliability, reduce set
Meter and production cost.
To realize above-mentioned purpose of design, the side for measuring beam pumping unit suspension point power indirectly based on motor power (output)
Method, in beam pumping unit four-bar mechanism, suspension point dynamic stress meets following formula:
I.e. under the premise of known electric motor power (P) and crank angle (θ), measurement acquires the real-time dynamic of suspension point indirectly
State stress value.
As described above, the method for being measured beam pumping unit suspension point power indirectly based on motor power (output) is had the advantage, that
1, realize a kind of new indirect type force measuring method, have compared to the prior art strong real-time, high reliablity, at
The feature that this is low, accuracy is high.
2, the real-time of oil well condition monitoring can be improved significantly on this basis, reflect polished rod load in time, displacement, add
The dynamic relationship of speed, having during beam pumping unit automation, information-based upgrading makes practical value.
Detailed description of the invention
Fig. 1 is the working principle diagram of beam pumping unit four-bar mechanism；
Fig. 2 is the relational graph between motor input torque and speed reducer output torque；
Fig. 3 is the schematic diagram based on the point suspension movement change in displacement period acquired in the application and pumping unit actual parameter；
Fig. 4 is the schematic diagram based on point suspension movement speed variation cycle acquired in the application and pumping unit actual parameter；
Fig. 5 is the schematic diagram based on the point suspension movement acceleration change period acquired in the application and pumping unit actual parameter.
Specific embodiment
Present invention will be further explained below with reference to the attached drawings and examples.
Embodiment 1, a method of it measuring beam pumping unit suspension point power indirectly based on motor power (output), is known walking beam
Under the premise of formula motor of oil extractor power P numerical value, exported by successively calculating motor input power and torque, speed reducer
Relationship between torque measures the real-time stress of suspension point in parallel motion model by crank angle θ indirectly
Change, i.e. the real-time tension variations situation that suspension point C is subject in Fig. 1.
As shown in Figure 1, the rectangular co-ordinate motion model schematic illustration of beam pumping unit four-bar mechanism.
In four-bar mechanism, O point is the fulcrum of beam pumping unit support shaft, O1Point is that beam pumping unit power is defeated
Enter the midpoint of axis, C point is the suspension point of beam pumping unit, and B point is the endpoint of pumping unit cross-beam of slide beam axis (walking beam postbrachium), A
Point is the endpoint of beam type oil pumping machine crank.
The course of work is that the power input shaft of motor transmits torque to A point by crank, and A point is around O1Point is with radius
It is that ω moves in a circle for R, angular speed, A point is connect with B point by connecting rod P, does B point under the drive of A point with radius M
Circular arc moves back and forth；C point and B point are the both ends of same beam (walking beam), do circular arc reciprocating motion, and the fortune of C point by fulcrum of O point
Dynamic direction is opposite with B point.
Wherein, R is crank length (unit: mm)；P is length of connecting rod (unit: mm)；I is that support shaft midpoint is defeated to power
Enter the horizontal distance (unit: mm) at axis midpoint；F is vertical range (unit: mm) of the support shaft midpoint to power input shaft midpoint；
M is length (unit: mm) of the support shaft midpoint O to crossbeam axis terminal B；N be support shaft midpoint O to suspension point C length (unit:
mm)。
The rotational angle theta of crank is turned in real time in rectangular coordinate system in the case where motor goes out the driving of torque by speed reducer
Angle.
Specific calculating process is as follows:
The relational expression set between the output power P and voltage U, electric current I of motor is as follows:
P=UI (1)
Wherein, the unit of power P is W, and the unit of voltage U is V, and the unit of electric current I is A.
The output torque T of motor is the torque for rotating oil pumping machine crank, abbreviation torque.Torque T and power P, revolving speed
The relational expression of n is as follows: T=9550P/n (2)
Thus it can also derive: P=Tn/9550 (3)
Wherein, the unit of power P is kW, and the unit of revolving speed n is r/min, and the unit of torque T is Nm, and 9550 be to calculate
The coefficient of constant value obtained.
It is that coefficient of constant value 9550 shifts process onto below:
Usually it is found that power P=torsion F* linear velocity V (1-1)
By torque T=torsion F* operating radius R, i.e. T=F*R, release F=T/R (1-2)
And/60=π R*n points/30 of linear velocity V=2 π R* revolving speed per second (n seconds)=2 every point of revolving speed of π R* (n points).
It obtains, V=π R*n/30 (1-3)
Formula (1-2), (1-3) are substituted into formula (1-1) and obtained:
P=F*V=T/R* π R*n/30=π * T*n/30
It is exactly following formula: P*1000=π/30*T*n if changing the unit of P into kW
That is, 30000/3.1415926*P=T*n
9549.297*P=T*n → T=9550P/n
By above formula (1), (3), electrical power P (unit kW) can be expressed from the next:
P=Tn/9550=UI/1000 (4)
It can be deformed into Tn/9.55=UI (5)
Also T=9.55UI/n (6) be can be deformed into
As shown in Fig. 2 the relation schematic diagram between motor input torque and speed reducer output torque.
The ratio of angular speed is transmission ratio, also referred to as speed ratio between motor and speed reducer.
That is, ε=n/n1 (7)
ε is transmission ratio, dimensionless in formula；N is the revolution that motor is inputted to speed reducer, unit r/min；n1For speed reducer
The revolution of output, unit r/min；
Speed reducer input torque T and output torque T1With following relationship:
That is the product of the torque T of speed reducer input shaft and its revolving speed n, the torque T with output shaft1With its revolving speed n1Product
It is equal.That is, Tn=T1·n1→T1=ε T (8)
In formula, ε is transmission ratio, dimensionless；T is motor input torque, unit Nm；T1For speed reducer output torque,
Unit Nm；
As shown in Figure 1, establishing rectangular coordinate system by zero point of O point, i.e. O point rectangular co-ordinate is (0,0), then O1The coordinate of point
For O1(- I ,-F), A point is with O1It is circled for the center of circle, angular velocity of satellite motion ω.Then have, (xa+I)2+(ya+F)2=R2 (9)
θ=ω t (10)
xa=Rcos θ-I (11)
ya=Rsin θ-F (12)
The then equation of motion of B point: xb 2+yb 2=M2 (13)
It is obtained by the range formula of A to B point:
(xb-xa)2+(yb-ya)2=P2 (14)
Formula (14) are unfolded:
xb 2+xa 2-2xbxa+yb 2+ya 2-2ybya=P2 (15)
Formula (15) ﹣ (9) ﹣ (13) is obtained:
-2xbxa-2Ixa-2ybya-2Fya=P2-M2-R2+F2+I2
2xbxa+2ybya=M2+R2-P2-F2-I2-2Ixa-2Fya
Formula (16) are substituted into formula (13):
If Q=(M2+R2-P2-F2-I2-2(xa-2Fya)/2, then have
It is solved by the relationship of quadratic equation with one unknown root and score:
By in figure it is found that | yb|≤R, i.e.-R≤yb≤R (18)
It is obtained by formula (9):
xa 2+ya 2=R2-2Ixa-2Fya (19)
(19) are substituted into formula (17):
Foundation linear equation, suspension point location of C:
Suspension point location of C curve graph as shown in Figure 3 passes through suspension point location of C coordinate value ycVariation, can find out suspension point C's
Speed Vc, i.e. VcIt is ycFirst derivative:
Speed curve diagram of the pumping unit hanging point C based on crank angle θ can be drawn out accordingly, as shown in Figure 4.
Based on identical principle, by the coordinate value y of suspension point CcObtain the acceleration a of suspension point Cc, i.e. acIt is ycSecond order lead
Number:
The acceleration plots of pumping unit hanging point (C) based on crank angle θ are drawn accordingly, as shown in Figure 5.
As shown in Figure 1, the power in A point is decomposed into following formula:
Fx=FAcosθ (24)
Fy=FAsinθ (25)
The total weight W, then torque T of suspension point C suspensionC
TC=W (g+a) N (26)
Similarly, in the torque of B point are as follows:
By above formula (8) it is found that the torque in A point meets following formula:
TA=ε T
Wherein T is the torque of motor；It is in the stress of A point then:
FA=TA/R (28)
It is using O as fulcrum and torque reaches balance due to B point and C point, then has:
TB=TC (29)
That is:
Therefore, the power that suspension point C is dynamically subject in real time may be expressed as:
By then suspension point C real-time stress is in above formula (8) and (6) T=9.55P/n substitution formula (30):
Wherein, xbIt is calculated by formula (16), then P is motor input power, and θ is that speed reducer drives turning for crank
Angle, n are motor revolution, and motor power (output) unit is kW.
Through above formula (31) it is found that on the basis of known electric motor input power P, then the rotational angle theta for passing through crank
It can should measure indirectly the situation of change of the real-time under tension of suspension point C.
As described above, similar technical solution can be derived in conjunction with the plan content that attached drawing and description provide.But it is all
Without departing from the plan content of structure of the invention, the interest field of technical solution of the present invention is still fallen within.
Claims (1)
1. a kind of method for measuring beam pumping unit suspension point power indirectly based on motor power (output), it is characterised in that: in beam type
In pumping unit four-bar mechanism, suspension point dynamic stress meets following formula,
Based on known electric motor power (P) and crank angle (θ), suspension point dynamic stress value in real time is measured indirectly.
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Cited By (2)
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| CN112761594A (en) * | 2021-02-04 | 2021-05-07 | 苏州伟创电气科技股份有限公司 | Method for acquiring rotation angle of crank, method for positioning bottom dead center and frequency converter |
| CN112783055A (en) * | 2021-01-04 | 2021-05-11 | 西安华瑞网电科技股份有限公司 | Online soft measurement method and device for suspension point load of beam-pumping unit |
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Cited By (2)
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| CN112783055A (en) * | 2021-01-04 | 2021-05-11 | 西安华瑞网电科技股份有限公司 | Online soft measurement method and device for suspension point load of beam-pumping unit |
| CN112761594A (en) * | 2021-02-04 | 2021-05-07 | 苏州伟创电气科技股份有限公司 | Method for acquiring rotation angle of crank, method for positioning bottom dead center and frequency converter |
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