CN113513310B - Method for determining assembly angle of torsion shaft of swing valve pulse generator - Google Patents
Method for determining assembly angle of torsion shaft of swing valve pulse generator Download PDFInfo
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- CN113513310B CN113513310B CN202110808709.4A CN202110808709A CN113513310B CN 113513310 B CN113513310 B CN 113513310B CN 202110808709 A CN202110808709 A CN 202110808709A CN 113513310 B CN113513310 B CN 113513310B
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- 238000000034 method Methods 0.000 title claims abstract description 25
- 238000006073 displacement reaction Methods 0.000 claims description 44
- 230000004044 response Effects 0.000 abstract description 7
- 239000002002 slurry Substances 0.000 description 9
- 238000005553 drilling Methods 0.000 description 5
- 238000004364 calculation method Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 3
- 238000009826 distribution Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
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- 238000004458 analytical method Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 238000004804 winding Methods 0.000 description 2
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 239000003209 petroleum derivative Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 230000008054 signal transmission Effects 0.000 description 1
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B47/00—Survey of boreholes or wells
- E21B47/12—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling
- E21B47/14—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling using acoustic waves
- E21B47/18—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling using acoustic waves through the well fluid, e.g. mud pressure pulse telemetry
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B47/00—Survey of boreholes or wells
- E21B47/12—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling
- E21B47/14—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling using acoustic waves
- E21B47/18—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling using acoustic waves through the well fluid, e.g. mud pressure pulse telemetry
- E21B47/20—Means for transmitting measuring-signals or control signals from the well to the surface, or from the surface to the well, e.g. for logging while drilling using acoustic waves through the well fluid, e.g. mud pressure pulse telemetry by modulation of mud waves, e.g. by continuous modulation
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Abstract
A method for determining a torsion shaft assembly angle of a swing valve pulse generator comprises a motor, a stator, a rotor and a torsion shaft, wherein the motor drives the torsion shaft, and the torsion shaft drives the rotor to rotate relative to the stator to generate a pulse signal; the method comprises the following steps: determining a maximum closing angle of the rotor when the pendulum valve pulser is unpowered; and determining the assembly angle of the torsion shaft, so that when the rotor is at the maximum closing angle, the torque generated by the torsion shaft is opposite to the hydraulic torque applied to the rotor in direction, and the value of the torque is not less than that of the hydraulic torque. The method for determining the assembly angle of the torsion shaft of the oscillating valve pulse generator provided by the embodiment of the disclosure can reasonably determine the assembly angle of the torsion shaft and can avoid pump holding. In addition, the power consumption of the swing valve pulse generator can be reduced as much as possible, and the response speed of the swing valve pulse generator can be improved.
Description
Technical Field
The present disclosure relates to a pendulum valve pulse generator, and more particularly, to a method of determining a torsion axis assembly angle of a pendulum valve pulse generator.
Background
In the process of drilling petroleum and natural gas, the measurement while drilling system plays an irreplaceable role in the aspects of improving drilling and production efficiency and shortening engineering period. The measurement while drilling system mainly comprises various underground parameter measuring instruments, an information transmission tool and a ground receiving tool, wherein a drilling fluid pulse method represented by continuous wave signal transmission in the information transmission system is widely concerned at home and abroad.
A pulse generator mechanism for swinging valve is composed of motor, torsion shaft, stator and rotor. The torsion shaft is driven by the direct current motor, and the torsion shaft drives the rotor to rotate to generate a pulse signal. The torsion shaft is used as a connecting piece of the driving motor and the rotor and a power transmission device. In the prior art, when the torsion shaft is assembled, a certain angle is usually directly selected for assembly, such as 0 degrees and 6 degrees. However, the assembly angles have the problems of large power consumption of the motor, slow response speed, pump holding and the like.
Disclosure of Invention
The following is a summary of the subject matter described in detail herein. This summary is not intended to limit the scope of the claims.
The embodiments of the present disclosure provide the following solutions.
A method for determining a torsion shaft assembly angle of a swing valve pulse generator comprises a motor, a stator, a rotor and a torsion shaft, wherein the motor drives the torsion shaft, and the torsion shaft drives the rotor to rotate to generate a pulse signal; the method comprises the following steps:
determining a maximum closing angle of the rotor when the pendulum valve pulser is not powered; the maximum closing angle is the maximum closing angle of the rotor when the rotor rotates from a fully open position to a closing direction and the swing pulser is capable of maintaining a normal displacement cycle;
determining an assembly angle of the torsion shaft, so that when the rotor is at the maximum closing angle, the torque generated by the torsion shaft is opposite to the hydraulic torque applied to the rotor, and the value of the torque is not less than the value of the hydraulic torque;
an assembly angle beta of the torsion shaft 0 The upper limit range is calculated by the following formula:
an assembly angle beta of the torsion shaft 0 A lower range calculated by the following formula:
wherein A is a set coefficient, A is more than or equal to 0.7 and less than or equal to 0.9, and theta C Is the maximum closing angle of the rotor, K is the stiffness coefficient of the torsion shaft, T H (θ C ) For rotating said rotor to theta C The hydraulic torque to which it is subjected.
The method for determining the assembly angle of the torsion shaft of the oscillating valve pulse generator provided by the embodiment of the disclosure can reasonably determine the assembly angle of the torsion shaft and can avoid pump holding. In addition, the power consumption of the oscillating valve pulse generator can be reduced as much as possible, and the response speed of the oscillating valve pulse generator can be improved.
Other aspects will be apparent upon reading and understanding the attached figures and detailed description.
Drawings
The accompanying drawings are included to provide a further understanding of the embodiments herein and are incorporated in and constitute a part of this specification, illustrate embodiments herein and are not to be construed as limiting the embodiments herein.
FIG. 1 is a schematic diagram of a pendulum valve pulse generator;
FIG. 2 is a schematic cross-sectional view of a stator and rotor of a pendulum valve pulser;
FIG. 3 is a graph illustrating the distribution of hydraulic torque along the rotor angle according to an embodiment of the present disclosure;
FIG. 4 shows an embodiment of the disclosure with a displacement of 2.0m 3 Distribution curve graphs of the balance torque along the rotor angle under different rotor assembly angles in min;
FIG. 5 is a graph of the distribution of the balance torque along the rotor angle at different displacements for a rotor assembly angle of 8.19 in accordance with an embodiment of the present disclosure.
Detailed Description
The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings in the embodiments of the present disclosure, and it is obvious that the described embodiments are only a part of the embodiments of the present disclosure, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments disclosed herein without inventive step, are intended to be within the scope of the present disclosure.
It should be noted that all the directional indications (such as up, down, left, right, front, and back) in the embodiments of the present disclosure are only used to explain the relative position relationship between the components, the motion situation, and the like in a specific posture (as shown in the drawings), and if the specific posture is changed, the directional indication is changed accordingly.
In addition, descriptions such as references to "first", "second", and the like in the embodiments of the present disclosure are for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicit ly indicating a number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present disclosure, "plurality" means at least two, e.g., two, three, etc., unless explicitly defined otherwise.
In the present disclosure, unless expressly stated or limited otherwise, the terms "connected," "secured," and the like are to be construed broadly, such that "secured" can be, for example, fixedly connected, releasably connected, or integral to one another; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be interconnected within two elements or in a relationship where two elements interact with each other unless otherwise specifically limited. The specific meaning of the above terms in the present disclosure can be understood by those of ordinary skill in the art as appropriate.
In addition, technical solutions in the embodiments of the present disclosure may be combined with each other, but must be based on the realization of the capability of a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present disclosure.
Fig. 1 is a schematic diagram of a pendulum valve pulse generator according to an embodiment of the present disclosure. As shown in fig. 1, the swing valve pulse generator provided by the embodiment of the present disclosure includes a motor 2, a torsion shaft 3, a coupler 4, a stator 5, and a rotor 6, which are mounted on a bearing 1, the torsion shaft 3 is driven by the motor 2, and the torsion shaft 3 drives the rotor 6 to rotate through the coupler 4 to generate a pulse signal. The mud flows from the side where the stator 5 is located to the side where the rotor 6 is located, the motor 2 drives the torsion shaft 3, the torsion shaft 3 drives the rotor 6 to rotate relative to the stator 5, the stator 5 and the rotor 6 of the oscillating valve pulse generator periodically block a fluid channel, and the mud passing through is sheared, so that a pulse signal (also called pressure wave) is generated. The torsion shaft 3 can be implemented as a torsion spring, for example.
The flow channel model of the slurry passing through the oscillating valve pulse generator is dispersed by adopting an unstructured grid, the grid updating is realized by adopting a moving grid technology due to the reciprocating motion of the rotor 6, and the flow field characteristics of the rotor 6 of the oscillating valve pulse generator under different rotating speed conditions are simulated by Fluent software. Under the condition that the flow field is stable, the momentum change of the slurry generates a steady-state hydraulic torque, so that the flow field can be simulated by controlling the rotor 6 to move at a constant speed or stop at different angles, and the steady-state hydraulic torque characteristic can be analyzed. The dynamic hydraulic torque is caused by the flow field change caused by the acceleration and deceleration of the rotor 6, and the dynamic hydraulic torque characteristic of the rotor 6 can be analyzed by controlling the rotor 6 to move under a certain acceleration. Through the fluid analysis of the stator and rotor calculation domains of the oscillating valve pulse generator, the following conclusions can be obtained: the hydraulic torque is distributed along the same direction, namely the rotor 6 is driven to move towards the closing direction; the hydraulic torque has close relation with the position of the rotor 6, and has smaller relation with the angular speed and the angular acceleration of the rotation of the rotor 6; the pressure wave change is mainly related to the flow, namely the valve port flow area; the influence of the rotation angle of the rotor 6 on the hydraulic torque is obvious, and the maximum hydraulic torque appears when the stator and the rotor are close to the closed position. According to theoretical analysis, a relation curve of hydraulic torque (steady-state hydraulic torque and dynamic hydraulic torque) and the rotation angle of the rotor can be obtained by combining with experimental tests. Under the same condition, the change rule of the dynamic hydraulic torque is basically the same as the steady-state hydraulic torque, and the amplitude is slightly lower than the steady-state hydraulic torque. Therefore, the hydraulic torque received by the rotor 6 in this embodiment may be calculated according to the steady-state hydraulic torque, and the margin of the calculation result may be increased while calculating according to the steady-state hydraulic torque, but may be calculated according to the dynamic hydraulic torque in other embodiments, or calculated according to the weighted value of the steady-state hydraulic torque and the dynamic hydraulic torque.
The inventor finds that the rigidity and the assembly angle of a torsion shaft 3 in the swing valve pulse generator directly influence the working effect of the pulse generator, the elastic deformation torque generated by the torsion shaft 3 when the swing valve pulse generator works can help the motor to overcome the external hydraulic torque, but if the restoring torque generated by the torsion shaft 3 due to deformation is too large, the load of the motor can be increased, and the effect of a mud pulse signal is influenced. For example, if a small angle is selected for assembly, there may be problems of excessive power consumption of the motor and slow response speed. If a larger angle of fit is chosen, if the hydraulic torque at that angle is greater than the torque of the torsion shaft, when the instrument is not powered or fails, the rotor 6 will tend to close under the action of the hydraulic torque, causing a pump hold. Therefore, it is necessary to provide a method for calculating and checking the torsion shaft 3 so that the torsion torque of the torsion shaft 3 and the hydraulic torque of the mud match the function of the motor.
Fig. 2 is a schematic cross-sectional view of the structure of the stator 5 and rotor 6 of the pendulum valve pulser according to an exemplary embodiment of the present application. In the illustrated exampleIn the middle, the vanes of the stator 5 and the vanes of the rotor 6 are all sector surfaces, the angles are all alpha, the opening angles are all gamma, and the torsion shaft assembly angle is beta 0 I.e. the initial angle between the stator blade and the rotor blade after installation: beta is not more than 0 degree 0 Gamma is less than or equal to gamma. In one example, the fan angles of the stator blade and the rotor blade are both 37 °, the opening angles are both 23 °, and 23 ° is hereinafter taken as an example of the opening angle, but the present application is not limited thereto.
In order to balance the hydraulic torque of the torsion shaft 3, the torsion shaft assembly angle β 0 Typically greater than 0. The swing valve pulse generator cannot be normally electrified to work at the beginning of starting the pump, and if the torsion shaft 3 is improperly assembled and the torque generated by the torsion shaft 3 cannot balance the hydraulic torque, the hydraulic torque may drive the rotor 6 to close, so that the pump is held back. Assuming that the stiffness coefficient of the torsion shaft 3 is K, when the angle of the rotor 6 is beta, the hydraulic torque is T H (beta) torque of torsion shaft T M (β)＝K·(β 0 - β), the equilibrium torque of the two being T (β): then there are:
T(β)＝T H (β)+T M (β)＝T H (β)+K·(β 0 -β)
when the balance torque T (β) > 0 indicates that the balance torque drives the rotor 6 to rotate in the closing direction of the swing valve pulse generator.
The application provides a method for determining a torsion shaft assembly angle of a swing valve pulse generator, which comprises the following steps:
determining a maximum closing angle of the rotor of the pendulum valve pulse generator when not powered;
and determining the assembly angle of the torsion shaft, so that when the rotor is at the maximum closing angle, the torque generated by the torsion shaft is opposite to the hydraulic torque applied to the rotor, and the torque value is not less than the hydraulic torque value.
In an exemplary embodiment of the present disclosure, after the design selection of the swing valve pulse generator is completed, by appropriately selecting the torsion shaft assembly angle, a certain opening degree of the rotor 6 is ensured before the swing valve pulse generator is powered on to work or in a fault condition, and a pump holding can be avoided. Suppose the wobble valve pulse generator is not in the working sceneThe maximum closing angle of the rotor 6 at the time of power-on (the maximum angle of rotation from the fully open position of the rotor 6 in the closing direction) is θ C (θ C < 23 °), the present embodiment defines the maximum closing angle as the maximum value of the closing angle of the rotor 6 when the oscillating valve pulser is able to maintain a normal displacement cycle, at which the corresponding steady-state hydraulic torque is noted as T H (θ C ) Then the conditions to avoid pumping in this example are:
T(θ C )＝K·(β 0 -θ C )+T H (θ C )≤0
the following can be obtained:
balance torque T (theta) C ) 0 or less means that the rotor angle is θ C When the torque is applied, the rotor 6 is not driven to rotate towards the closing direction under the combined action of the steady-state hydraulic torque and the torque of the torsion shaft, so that the rotor 6 is prevented from rotating to be more than theta C The angle of the oscillating valve pulse generator makes it difficult to maintain normal displacement, resulting in pump holding. That is, the maximum closing angle of the rotor 6 when not being electrified is θ C In the meantime, for the torsion shaft 3 with the rigidity coefficient of K, the assembly angle beta of the torsion shaft of the pump can be avoided 0 Can not exceed a maximum value of
In an example, it is assumed that the rotor 6 is controlled in a segmented sinusoidal manner, that is, a certain voltage is applied to the motor winding to generate a segmented sinusoidal current in the motor winding, and the purpose of controlling the motor torque is achieved by controlling the amplitude and the phase of the sinusoidal current. When the pendulum valve pulser is operating normally (i.e. displacement is normal), its equivalent flow area is about 33% of that when the rotor 6 is fully open, i.e. the maximum closing angle of the rotor 6 is set to 67% of the vane opening angle of the stator 5, corresponding to a rotor angle of 23 ° + 0.67=15.41 °, so when the rotor maximum closing angle θ is normal C A pulse generator capable of maintaining a normal displacement cycle at =15.41,theta determined from this example C The assembly angle beta of the torsion shaft is substituted into the solution 0 The formula (1) can obtain that the assembling angle of the torsion shaft at the moment is as follows:
by further determining the hydraulic torque at 15.41 ° of the rotor 6 and the stiffness factor of the torsion shaft 3, a specific torsion shaft assembly angle β can be determined 0 。
The torsion shaft assembly angle beta 0 The maximum assembly angle at which the torsion bar 3 is assembled. I.e. if the torsion axis assembly angle exceeds beta 0 When the motor is not electrified or the oscillating valve pulse generator fails, the torque of the torsion shaft cannot completely resist the steady-state hydraulic torque, and the oscillating valve pulse generator cannot maintain normal displacement circulation. However, if the assembly angle β of the torsion bar 3 is large 0 If the torque is too small, the torque generated by the torsion shaft 3 due to deformation is too large, so that the load of the motor is increased, and the effect of a mud pulse signal is influenced. Therefore, on the premise of preventing the pump from being held back, the assembly angle beta of the torsion shaft 0 Nor too small. Thus, the torsion shaft assembling angle beta is determined 0 The lower limit of the value of (3) is further defined after the upper limit of (3). In an exemplary embodiment of the present disclosure, the assembly angle of the torsion bar
Wherein A is a set coefficient. Further, the coefficient A can range from 0.7 ≦ A ≦ 0.9.
FIG. 3 is a graph illustrating an exemplary embodiment of the present disclosure with mud displacement of 1.8m, respectively 3 Min and 2.0m 3 The hydraulic torque of the rotor 6 under different angles under the min working condition. In this embodiment, the gap between the stator 5 and the rotor 6 is 1.26mm. Taking the torsional axis stiffness coefficient K =10/24N · m/° as an example, when the rotor 6 is at the maximum closing angle of 15.41 °, the hydraulic torque is 2.3635N · m (the mud displacement is 1.8 m) respectively 3 Min) and 3.0061 N.m (mud discharge capacity of 2.0 m) 3 At/min), calculated from the aboveFormula of torsion shaft assembly angle can be used for obtaining rotor assembly angle beta of swing valve pulse generator 0 9.7377 deg. and 8.1953 deg., respectively. In other words, in the present embodiment, when the torsion axis fitting angle does not exceed 9.7377 °, even if the instrument is powered off, it is possible to ensure the displacement amounts to be 1.8m, respectively 3 Pump holding phenomenon does not occur at/min. When the torsion shaft assembly angle does not exceed 8.1953 deg., the displacement of 2.0m can be ensured even if the instrument is powered off 3 No pump holding phenomenon occurs during the/min.
The discharge capacity of the slurry is 2.0m 3 The calculation result at/min is an example, and the balance torque acting on the rotor 6 by the hydraulic torque and the torsion shaft torque when the rotor attachment angle is increased or decreased is shown in fig. 4. As can be seen from FIG. 4, when β is 0 At about 8.19 deg., at 2.0m 3 In the case of a/min displacement power failure, the rotor 6 is at a balance torque of 0 at 10 ° to 16 °, and the rotor 6 is oscillating approximately between 10 ° to 16 °. At the moment, the rotor 6 is controlled by the motor to swing around the angle range, so that when the mud is sheared to generate a pulse signal, the balance torque to be overcome is small, the power consumption is low, and the response speed is high.
If beta is 0 When the rotor 6 is closed at an angle of about 20 °, the balance torque becomes 0, and the rotor 6 is opened at an angle (the angle from the current position of the rotor to the fully closed position) of only about 3 °. If beta is 0 When the angle of the rotor 6 is reduced to 7 °, the equilibrium torque becomes 0 when the closing angle of the rotor 6 is around 5 °, and the opening angle of the rotor 6 becomes large, and can be maintained at about 18 °. It can be seen that beta is reduced 0 The opening angle of the rotor 6 is increased, the stator 5 and the rotor 6 can provide larger flow area for slurry to pass through, but the balance torque required to be overcome when the rotor 6 is at a higher angle is increased (because the torque is increased), so that the power consumption is increased, and the response speed is reduced; on the contrary, if beta is increased 0 The opening angle of the rotor 6 is reduced, so that the flow area of the slurry is reduced, and a pump holding phenomenon may be caused.
Similarly, the above-mentioned slurry discharge amounts were 1.8 and 2.0m, respectively 3 The result of the/min calculation is for example when a larger displacement (2.0 m in the example) is used 3 Min) calculating rotor assemblyAfter the angle is matched, the rotor assembly angle is directly applied to a working condition with smaller displacement (1.8 m in the example) 3 /min), when the rotor is fitted at an angle β, as shown in FIG. 5 0 About 8.19 deg., if the displacement is reduced to 1.8m 3 Min, the opening angle of the rotor 6 is increased to a certain extent and can be kept at about 14 degrees, and the maximum closing angle of the rotor 6 is about 9 degrees; on the contrary, if the displacement is increased more than 2.0m 3 Min, the opening angle of the rotor 6 is reduced, i.e. the maximum closing angle of the rotor 6 exceeds the angle that can maintain the normal circulation of the displacement, i.e. more than 15.41 °, in which case the flow area of the slurry becomes smaller, possibly resulting in pump failure.
If the pendulum valve pulser has multiple displacement conditions, the hydraulic torque may be calculated from the hydraulic torque experienced by the pendulum valve pulser at the highest displacement condition of the multiple displacements. If the oscillating valve pulse generator has three working conditions of high displacement, medium displacement and low displacement, the hydraulic torque can also be calculated according to the hydraulic torque received by the oscillating valve pulse generator when the oscillating valve pulse generator is in the medium displacement working condition.
In an exemplary embodiment of the present disclosure, the mud displacement is divided into 1.8 and 2.0m 3 And/min under two different working conditions. When 2.0m is adopted 3 When the rotor assembly angle is calculated by the min discharge capacity, the initial slurry discharge capacity is 1.8 or 2.0m no matter the pump is started 3 Every min, the pump can be prevented from being held; when the instrument fails, the mud discharge amount does not need to be changed from 2.0m 3 The/min is reduced to 1.8m 3 The maximum closing angle of the rotor 6 is also able to maintain the angle of displacement normal circulation.
When using 1.8m 3 When the rotor assembly angle is calculated by the displacement per minute, the swing valve pulse generator can be normally opened and closed under the normal working condition of the motor 2, but the motor 2 is not normally powered up at the initial stage of pump starting, and if the displacement of mud is set to be 2.0m at the moment 3 Min, there is a risk of pump holding, so to avoid pump holding in the early stage of pump opening, the initial stage slurry discharge should be set to 1.8m 3 The discharge capacity per minute; similarly, when the instrument fails, the displacement should be reduced to 1.8m 3 Min preventing pump holding.
The method for determining the assembly angle of the torsion shaft of the oscillating valve pulse generator provided by the embodiment of the disclosure can reasonably determine the assembly angle of the torsion shaft, can reduce the power consumption of the oscillating valve pulse generator as much as possible on the premise of avoiding pump holding, and improves the response speed of the oscillating valve pulse generator.
The application still provides a swing valve pulse generator, and this swing valve pulse generator includes motor, stator, rotor and twist shaft, and the motor passes through the twist shaft and drives the rotor and rotate for the stator. The assembling angle of the torsion shaft is determined according to the method for determining the assembling angle of the torsion shaft of the swing valve pulse generator.
Although the embodiments disclosed in the present disclosure are described above, the descriptions are only for the convenience of understanding the present disclosure, and are not intended to limit the present disclosure. It will be understood by those skilled in the art of the present disclosure that various changes in form and details may be made therein without departing from the spirit and scope of the present disclosure, and that the scope of the present disclosure is to be limited only by the terms of the appended claims.
Claims (7)
1. A method for determining a torsion shaft assembly angle of a swing valve pulse generator comprises a motor, a stator, a rotor and a torsion shaft, wherein the motor drives the torsion shaft, and the torsion shaft drives the rotor to rotate relative to the stator to generate a pulse signal; the method comprises the following steps:
determining a maximum closing angle of the rotor when the pendulum valve pulser is unpowered; the maximum closing angle is the maximum value of the closing angle of the rotor when the rotor rotates from a fully open position to a closing direction and the swing pulser is capable of maintaining a normal displacement cycle;
determining an assembly angle of the torsion shaft, so that when the rotor is at the maximum closing angle, the torque generated by the torsion shaft is opposite to the hydraulic torque applied to the rotor, and the value of the torque is not less than the value of the hydraulic torque;
an assembly angle beta of the torsion shaft 0 The upper limit range is calculated by the following formula:
an assembly angle beta of the torsion shaft 0 A lower range calculated by the following formula:
wherein A is a set coefficient, A is more than or equal to 0.7 and less than or equal to 0.9, and theta C Is the maximum closing angle of the rotor, K is the stiffness coefficient of the torsion shaft, T H (θ C ) For the rotor to rotate to theta C The hydraulic torque to which it is subjected.
2. The method of claim 1, wherein: the rotor is controlled in a segmented sinusoidal manner, and the maximum closing angle of the rotor is set to 67% of the opening angle of the vanes of the stator.
3. The method of claim 1, wherein: the hydraulic torque is a steady state hydraulic torque.
4. The method of claim 1, wherein:
the swing valve pulse generator has a plurality of displacement conditions, and the hydraulic torque is calculated according to the hydraulic torque received by the swing valve pulse generator when the swing valve pulse generator is in the highest displacement condition of the plurality of displacement conditions.
5. The method of claim 1, wherein:
the swing valve pulse generator has three working conditions of high displacement, medium displacement and low displacement, and the hydraulic torque is calculated according to the hydraulic torque received when the swing valve pulse generator is in the medium displacement working condition.
6. A control method of a pendulum valve pulse generator whose torsion axis assembly angle is determined according to the method as set forth in claim 5, the control method comprising:
when the swing valve pulse generator is started, the swing valve pulse generator is started to the working condition of medium displacement or low displacement, and after the motor is normally electrified and works, the swing valve pulse generator is started to the working condition of high displacement so as to prevent pump holding; and
and when the work of the swing valve pulse generator fails, reducing the displacement of the swing valve pulse generator to the medium displacement or the low displacement so as to prevent the pump from being held.
7. A pendulum valve pulser comprising an electric motor, a stator, a rotor, and a torsion shaft, said electric motor rotating said rotor relative to said stator via said torsion shaft, said torsion shaft being angularly assembled in accordance with the method of any of claims 1 to 5.
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103696762A (en) * | 2013-12-29 | 2014-04-02 | 中国石油集团渤海钻探工程有限公司 | Rotation-driven swing valve type continuous wave generator |
| CN106958442A (en) * | 2017-05-04 | 2017-07-18 | 中国海洋石油总公司 | A kind of mud-pulse Transmission system and method |
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