RU2381383C1 - Method to produce oil using rod-type downhole pump and jack to this end (versions) - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: invention relates to oil production and can be used in reciprocation rod-type downhole pump (RDHP) using jacks as drives. In compliance with proposed method, crank rpm and rod reciprocation speed matched therewith are varied by sine law in smoothly accelerating operating stroke, whereat rod up travel reaches maximum speed with con rod in vertical position and crank at lower point. Idling is proportionally decelerated, whereat rod down travel reaches minimum speed with con rod in vertical position and crank at lower point. Con rod speed at operating stroke start and idling end is decreased by magnitude smaller than mean rod reciprocation speed. Proposed jack has cranks arranged on rims running in rolling supports (or roller bearings) fitted along perimetres of openings. The latter are arranged in vertical frames fastened on opposite side of support frame. Reduction gear and motor are arranged on frame-platform mounted on support frame to move along rocker beam direction. Reduction gear output shaft extensions support hubs in the plane of rims revolution, hubs OD being smaller than rim ID. Drive rods are attached to said hubs. Every said hub has through radial or inclined groove to accommodate roller fitted on pin pressed on the end face of appropriate rim with 90°-advance along the direction of rotation, as well as with smaller or greater advance with respect to the point of attachment to crank rim.

EFFECT: higher efficiency of oil production with no deterioration in process dynamics.

8 cl, 39 dwg

Description

The invention relates to the field of the oil industry and can be used in the operation of wells with sucker rod pumps (SHG) of reciprocating action using rocking machines as a drive, allowing, with the aim of increasing the productivity of borehole sucker rod pumping units (SHNU), to change the speed of up and down within each swing cycle of the wellhead rod with the suspension of the string of pump rods connected to the SHG plunger.

There is a method of operating wells with plunger deep pumps with the possibility of setting non-linear up-down speeds of the wellhead of the rocking machine within a single swing cycle (see V.N. Ivanovsky, V.I. Darishchev, A.A. Sabirov, V.S. .Kashtanov, SS Pekin. Well pumping units for oil production. M: State Unitary Enterprise Oil and Gas Publishing House of the Gubkin Russian State University of Oil and Gas, 2002 [1]).

The disadvantage of this method is the lack of coordination with the specific law of change in the non-linear speeds of raising and lowering the wellhead rod of the rocking machine and the duration of each swing cycle.

Known rocking machine with a drive Mark II (see [1]), equipped with a deaxial mechanism, in which, in order to increase the "traction" of the lever system, the crosshead of the rocking machine is located in front of the gearbox, close to the head of the balancer, and the special design of the crank and its location allow you to change the application of the moment created by the crank, relative to the moment created by the weight of the string of pump rods.

This device is characterized by the above-mentioned disadvantages, which limit the productivity of oil production and the motivation of manufacturers to a wider use of deep rod pumps with pumping units as a drive.

Closest to the invention in terms of the method is the operation of wells by Lufkin plunger deep-well pumps (see [1]), in which the upstream stroke time of the wellhead is increased due to a decrease in acceleration at the beginning of the upward stroke. This solution allows to reduce overloads on the drive and on the sucker rods in the most intense period of the cycle, which is the beginning of the upward stroke. The disadvantages of this method are:

a) lack of coordination with the specific law of acceleration reduction at the beginning of the upward move, as is the case with analogues;

b) a decrease in the productivity of the pumping unit due to the increase in travel time up.

Closest to the invention, the device is a rocking machine with an asynchronous electric motor, the operation of which is controlled by the control station SUS Triol 01 (see [1]). This drive provides a smooth, stepless speed control of an asynchronous electric motor with a power of 3 to 37 kW in the range from 0 to the nominal value (1500 rpm) and, as a result, non-linear stem lifting and lowering speeds.

The disadvantages of this device:

a) the limited variation in the frequency of rotation of the electric motor within each swing cycle is up to 40%;

b) overload and overheating of the induction motor as the speed deviates from the nominal value;

c) the above adverse operating conditions can lead to vibrations and premature failure of the equipment.

The objective of the invention is the creation of a method of oil production and a rocking machine for its implementation, devoid of the disadvantages of analogues and prototype.

The technical result achieved by using the proposed group of inventions is to increase the productivity of oil production without compromising the dynamics of the process.

This is achieved by the fact that in the method of oil production using SHGN, including changing the rotational speed of the crank of the rocking machine and coordinated with it through changing the angular velocity of the rocker balancer, changing the speed of the reciprocating motion of the wellhead rod, according to the proposed rotational speed of the crank and the speed matched with it the reciprocating movement of the wellhead rod is changed according to a sinusoidal law, smoothly accelerating the working stroke, in which the upward movement of the rod reaches max the maximum speed at the vertical position of the connecting rod and crank at the lower point, and proportionally slowing down the idle speed, at which the translational movement of the rod down reaches the minimum speed at the vertical position of the connecting rod and crank at the upper point, while the speed of the rod at the beginning of the working stroke and at the end of idling reduced by an amount less than the average velocity of the reciprocating motion of the rod.

The proposed set of features of the method of oil production ensures the achievement of the specified technical result, which is explained below.

Changing the speeds of the crank and the wellhead according to the sinusoidal law allows you to significantly, but smoothly, according to the sinusoidal dependence, increase the speed of the stroke to values that do not harm the dynamics of the process as a whole, with a subsequent decrease in speed during idling down the same sinusoidal dependence. As a result, a significant (up to two times or more) excess of the average crank rotation speed and, correspondingly, the average speed of the reciprocating movement of the rod with the cable suspension relative to the typical values of these values adopted by traditional technologies is ensured. In addition, a significant reduction in overloads on the sucker rods and the drive as a whole, which occurs at the end of idle down and at the beginning of the up stroke using traditional technologies, is achieved.

The decrease in the speed of the rod at the beginning of the stroke up and at the end of idle down by an amount less than the average speed of the reciprocating motion reduces adverse dynamic loads, thereby providing higher performance compared to the prototype. It happens as follows. At the beginning of the working stroke, when the rod with the rope suspension is already starting to move up, the pump plunger at the bottom of the pump rod string continues to move downward for some time due to its own weight and inertia of the movement of the entire mass of the pump rods. This creates cyclic peak dynamic loads, smoothing of which can effectively implement the proposed method due to some reduction (by the amount indicated above) of the speed at the end of idling and at the beginning of the working stroke at the lower point of the rod. This decrease in the stem velocity is fully compensated by acceleration with a smooth increase in speed upward according to a sinusoidal law with already established dynamics.

Technically, the solution of this problem is realized by introducing into the kinematics of a typical rocking machine an additional link that provides a shift of the axis of rotation of the output shaft of the gearbox relative to the axis of rotation of the crank. The specified offset forms an eccentricity, a change in the magnitude of which entails a change in the speed of rotation of the crank and the associated velocity of the reciprocating movement of the wellhead. Accordingly, with an increase in eccentricity, the swing frequency of the balancer increases, and, as a result, the overall performance of the installation as a whole. In the proposed invention, the additional link can be made in two ways: in the “pushing” application of torque with the installation of a hard link in the form of a carrier and a roller pivotally mounted on the end of the rim, as well as in the “pulling” application of torque with the installation of a flexible link in in the form of a pulling rope.

The technical result is achieved in that in a rocking machine for oil production using a sucker rod pump, including a support frame, a stand on which a balancer is mounted using a hinge, having, on the one hand, a head with a cable suspension and a wellhead, and, with on the other hand, a hinged traverse with connecting rods spaced on both sides of the rack, each of which is connected to a crank on which the counterweight is mounted, as well as a gearbox, the input shaft of which is connected to asyn via a V-belt transmission according to the invention, the cranks are mounted on rims which are mounted with the possibility of circular motion in the frame of roller bearings (or roller bearings) placed around the perimeters of windows made in vertical frames that are mounted on opposite sides of the support frame, and the gearbox and electric motor are mounted on a platform frame mounted on a support frame with the ability to move along the direction of the balancer, and at the ends of the output shaft of the gearbox in a circular motion plane Hubs are mounted, the outer diameter of which is made smaller than the inner radius of the rims, while carriers are attached to the hubs, each of which has a through radial or inclined groove, inside which a roller is placed pivotally (using a bearing) on a finger pressed into the end of the corresponding rim ahead of the rotation direction by an angle of 90 degrees, as well as less or more than this value, relative to the axis of attachment to the rim of the crank.

Through radial grooves of the carrier may have at the ends remote from the axis of rotation of the hub, smooth bends against the direction of rotation.

Through inclined carrier grooves can be made with a deviation in the direction of rotation of the end of the groove remote from the axis of rotation of the hub.

Through carrier grooves are made curved either in the form of an arc of a circle, or in the form of another smooth geometric dependence.

Through carrier grooves are made in the form of a combination of straight and curved sections.

Instead of a roller, a slider can also be placed inside the through groove of each carrier, also inserted through a hinge (for example, a rolling bearing) onto a finger pressed into the end of the corresponding rim.

The technical result is also achieved by the fact that in the rocking machine for oil production using a sucker rod pump, including a support frame, a stand on which a balancer is mounted using a hinge, having, on the one hand, a head with a cable suspension and a wellhead, and on the other hand, a hinged traverse with connecting rods spaced on both sides of the traverse connected to the crank on which the counterweight is mounted, as well as a gearbox, the input shaft of which is connected to the electric drive via V-belt transmission with a collar according to the invention, the cranks are mounted on rims which are mounted with the possibility of circular motion in the frame of rollers (or roller bearings) placed around the perimeters of windows made in vertical frames, which are rigidly attached to opposite sides of the support frame, the gearbox and motor being rigidly fixed to a platform frame mounted on a support frame with the ability to move along the direction of the balancer, and on the ends of the output shaft of the gearbox in the plane of the circular motion of the rims there are hubs whose outer diameter is smaller than the inner radius of the rims, while an outer groove is made along the outer diameter of each of the hubs, into which the pulling rope is laid, pivotally attached to the hub at one end, and also connected to the corresponding rim by a hinge installed with advancing in the direction of rotation by an angle of 90 degrees, as well as less or more than this value, relative to the attachment point to the rim of the crank.

The pulling ropes laid in the annular grooves of the respective hubs are pre-screwed onto the hubs by an amount that ensures uniform load transfer along the arc of coverage of the outer diameters of the hubs during tension, but not exceeding the full perimeter of the outer circumference of the hubs.

The radii of the annular grooves in their cross section, made on the outer diameters of each of the hubs, correspond to the radii of the pulling ropes with the necessary clearance for unhindered laying and tight fit to the groove.

The proposed set of features of a device for oil production ensures the achievement of the specified technical result as follows.

Supplementing the device, on the one hand, with rims mounted to rotate in the frame of roller bearings (or roller bearings), placed around the perimeters of windows, made in vertical frames, which are rigidly attached on opposite sides to a support frame fixed on piles, fixed to crank rims, and on the other hand, mounting the gearbox and electric motor on a platform frame mounted to move along the support frame along the balancer, with simultaneous installation at the ends the output shaft of the hub reducer provides the possibility of displacement of the axis of rotation of these hubs relative to the axis of rotation of the cranks. In this way an eccentricity is formed, the change of which makes it possible, through a change in the frequency of rocking of the balancer, to change the overall performance of USGN.

Complementing the device with carriers mounted on the hubs or, alternatively, with pulling ropes ensures the rotation of the rims with a frequency that can be changed according to a sinusoidal law.

The condition of advancing in the direction of rotation of the attachment point to the paired rims of the finger on which the roller is pivotally mounted, placed in the radial through groove of the carrier (or, alternatively, the pivot points of the pulling rope with the rim), relative to the axis of attachment on the corresponding rim of the crank, provides a relative reduction the speed of the working stroke at its finish when advancing by an angle less than 90 degrees, and, accordingly, the increase in the speed of the working move at its finish when advancing by an angle greater than 90 degrees.

Performing through radial grooves of the carrier with a smooth bend against the direction of rotation at the end remote from the axis of the hub allows you to reduce the speed of the working stroke of the wellhead rod at the finish of the working stroke and the corresponding smooth decrease in the frequency of rotation of the rim even when the balancer head approaches its highest swing point.

Performing inclined through the grooves of the carrier with a deviation as it moves away from the axis of the hubs in the direction of rotation allows you to further increase the average frequency of rotation of the rim relative to the hub and, accordingly, increase the productivity of oil production.

The implementation of through grooves drove curved either in the form of an arc of a circle, or in the form of another smooth geometric dependence, or in the form of a combination of straight and curved sections allows you to further improve the dynamics of the swing process.

The execution inside the through (both radial and inclined) groove of each carrier instead of the roller of the slider, also inserted through a hinge (for example, a rolling bearing) on a finger pressed into the end of the corresponding rim, allows to reduce contact stress, since the slider slides along its entire adjacent the lateral surface along the incident inner surface of the through groove drove in the process of transmitting torque.

The pulling ropes laid in the annular grooves of the hubs are pre-screwed onto the hubs by an amount that ensures uniform load transfer along the arc of coverage of the outer diameters of the hubs during tensioning, but not exceeding the full perimeter of the outer circumference of the hub, in order to exclude the winding of each rope itself in the process of each complete revolution relative to its own axis of rotation. In addition, the radius of the groove grooves on the hubs in cross section should correspond to the radius of the pulling rope with the necessary clearance for unhindered laying and tight fit to the groove, which ensures a smooth redistribution of the load along the contact arc.

These distinctive features are not known in the applied methods of oil production using deep rod pumps and pumping units for their implementation.

The essence of the proposed group of inventions is illustrated by drawings, which depict:

figure 1 is a side view of the rocking machine with a shift of the axis of rotation of the hub mounted on the output shaft of the gearbox relative to the axis of rotation of the rim rigidly connected to the crank, towards the head of the balancer by the amount of eccentricity e (use case);

figure 2 is a side view of the rocking machine with the displacement of the hub mounted on the output shaft of the gearbox relative to the rim rigidly connected to the crank towards the head of the balancer by the amount of eccentricity e (use case of the traction rope);

figure 3 is a rear view of the rocking machine (use case traction rope);

figure 4 is a graphical dependence of the change in time t of the rotational speed n _var clockwise of the rim and the distance R _var from the attachment point to the rim of the roller that receives torque from the carrier (or traction rope) to the axis of rotation of the hub;

figure 5 is a graphical dependence of the change in time t of the speed V _{var of the} reciprocating movement of the cable suspension with wellhead rod and the clockwise rotation speed of the rim n _var ;

Fig.6 is a location diagram of a roller mounted on the rim located inside the through radial groove of the carrier, with a minimum distance R _{var min} from the axis of the roller to the axis of rotation of the hub and the corresponding arrangement of the balancer with the head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.6;

Fig.7 is a location diagram of a roller mounted on the rim located inside the through radial groove of the carrier, when the rim rotates clockwise 90 degrees relative to the location in Fig.6 and the corresponding location of the balancer with head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.7;

Fig. 8 is an arrangement diagram of a roller mounted on the rim located inside the through radial groove of the carrier when turning the rim clockwise by 180 degrees relative to the arrangement in Fig. 6, in which the distance from the axis of the roller to the axis of rotation of the hub has a maximum value of Rvar _max , and the corresponding arrangement of the balancer with the head, connecting rod and crank; on figa is a graph of the variation of the rim speed n _var in time t when positioning according to Fig.8;

Fig.9 is a location diagram of a roller mounted on the rim located inside the through radial groove of the carrier attached to the hub when the rim is rotated clockwise by 270 degrees relative to the location in Fig.6 and the corresponding arrangement of the balancer with the head, connecting rod and crank; Fig. 9a is a graph of the variation of the rim rotation speed n _var in time t during positioning according to Fig. 9;

figure 10 - arrangement of the mounted on the rim of the roller placed inside the through radial groove of the carrier, when the rim is rotated clockwise 360 degrees relative to the location in Fig.6 and the corresponding location of the balancer with head, connecting rod and crank; on figa is a graph of the change in the rpm rotation speed n _var in time t when positioning according to figure 10;

11 is a location diagram of a roller mounted on a rim located inside a through inclined carrier groove attached to a hub with a minimum distance R _{var min} from the roller axis to the axis of rotation of the hub; on figa - the location of the mounted on the rim of the roller placed inside the through inclined groove of the carrier, when the rim is rotated clockwise 180 degrees, at which the distance from the axis of the roller to the axis of rotation of the hub has a maximum value of R _{var max} ;

on Fig - arrangement of the roller mounted on the rim, placed inside the through radial groove of the carrier with its smooth bend to the side,

opposite to rotation, with a minimum distance Rvar _min from the axis of the roller to the axis of rotation of the hub; on figa - arrangement of the roller mounted on the rim, placed inside the through radial groove of the carrier with its smooth bend in the direction opposite to rotation, when the rim is rotated clockwise 180 degrees, at which the distance from the axis of the roller to the axis of rotation of the hub has a maximum Rvar _max value;

in Fig.13 - location diagram of the slider mounted on the rim located inside the through inclined groove of the carrier, with a minimum distance R _{var min} from the axis of the slider to the axis of rotation of the hub; on figa - arrangement of the slider mounted on the rim located inside the through radial groove of the carrier, when the rim rotates clockwise 180 degrees, at which the distance from the axis of the slider to the axis of rotation of the hub has a maximum value of Rvar _max ;

on Fig - arrangement of the swivel of the pulling rope on the rim with a minimum distance R _{var min} from the swivel to the axis of rotation of the hub and the corresponding location of the balancer with the head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.14;

on Fig - arrangement of the swivel of the pulling rope on the rim when the rim is rotated clockwise by 45 degrees relative to Fig and the corresponding location of the balancer with the head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.15;

on Fig - arrangement of the swivel of the pulling rope on the rim when the rim is rotated clockwise 90 degrees relative to Fig, and the corresponding location of the balancer with the head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.16;

on Fig - arrangement of the swivel of the pulling rope on the rim when the rim rotates clockwise 135 degrees relative to Fig and the corresponding location of the balancer with the head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.17;

on Fig - location of the swivel of the pulling rope on the rim when the rim is rotated clockwise 180 degrees relative to Fig and the corresponding location of the balancer with the head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.18;

on Fig - arrangement of the swivel of the pulling rope on the rim when the rim is rotated clockwise 225 degrees relative to Fig and the corresponding location of the balancer with the head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.19;

on Fig - arrangement of the swivel of the pulling rope on the rim when the rim is rotated clockwise by 270 degrees relative to Fig and the corresponding location of the balancer with the head, connecting rod and crank; on figa is a graph of the variation of the rim speed n _var in time t when positioning according to Fig.20;

on Fig - arrangement of the swivel of the pulling rope on the rim when the rim is rotated clockwise 315 degrees relative to Fig and the corresponding location of the balancer with the head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.21;

on Fig - arrangement of the swivel of the pulling rope on the rim when the rim is rotated clockwise 360 degrees relative to Fig and the corresponding location of the balancer with the head, connecting rod and crank; on figa is a graph of the change in the frequency of rotation of the rim n _var in time t when positioning according to Fig.22.

The proposed rocking machine (see FIGS. 1, 2, 3) contains a support frame 1 on which the rack 2 is rigidly fixed. A balancer 3 is pivotally mounted on top of the rack 2. A head 4 is mounted at one end of the balancer 3 to which the cable suspension 5 is attached with the wellhead 6. At the opposite end, the balancer 3 is pivotally connected through the yoke 7 to the connecting rods 8, which are spaced on both sides of the strut 2. In turn, each of the connecting rods 8 is connected to the cranks 10, on which the balances 9 are mounted with relative displacement.

The input shaft of the gearbox 11 by means of a V-belt drive 12 is connected to an asynchronous electric motor 13, which drives the rocking machine through the above nodes and gears. The gearbox 11 and the motor 13 are rigidly mounted on the platform frame 14, which is mounted on the support frame 1 with the possibility of movement along the direction of the balancer 3. Fixing the relative displacement of the movable platform frame 14 along the support frame 1 when setting the calculated value of the eccentricity e is carried out using a positioning bar 15 using the mounting fingers 16, followed by bolting the platform frame 14 to the support frame 1.

Two vertical frames 17 spaced apart on both sides of the gearbox 11 are also fixed to the supporting frame 1 with round windows made therein, along which the roller bearings 18 are located. The windows of the vertical frames 17 can be rotated around the roller bearings 18 with 19 s ensuring the alignment of the rims between themselves and the location of the axis of the rims in the same plane with the axis of the swivel joint of the balancer 3 with the connecting rods 8.

Cranks 10 are rigidly attached to the rims 19, which are mounted directly on the output shaft of the gearbox in a typical rocking machine. In the proposed rocking machine, on the output shaft of the gearbox 11, at opposite ends of the shaft, hubs 20 are mounted, the outer diameter of which is made smaller than the inner radius of the rims 19 and which rotate in the planes of circular motion of the respective rims.

The proposed rocking machine has two options for providing an eccentricity of an additional link: pushing (“rigid”) - with a carrier set and pulling (flexible) - with a pulling rope installed.

So, according to a variant of the pushing additional link, carriers 21 are attached to the ends of the hubs 20, each of which has a through groove 22. Through grooves 22 can be made with different configurations: radial; radial with a smooth bend against the direction of rotation at the end remote from the axis of the hub 20; inclined with a deviation in the direction of rotation of the end of the groove 22, remote from the axis of rotation of the hub 20; curved either in the form of an arc of a circle, or in the form of another smooth geometric dependence; in the form of a combination of straight and curved sections.

Inside each of the through grooves 22, a roller 23 is placed, mounted through a hinge (for example, a rolling bearing) on a finger that is rigidly pressed into the end of the corresponding rim 19. Moreover, the through grooves 22 should begin at a distance from the axis of rotation of the hub 20, less than the difference between the radius of the axis fastening single fingers on the rim 19, taking into account the outer radius of the roller 23 and the maximum eccentricity, and end at a distance from the axis of rotation of the hub 20, greater than the sum of the radius of the axis of fastening of single fingers on the rim 19, taking into account the outward radius of the roller 23 and maximum eccentricity. In this case, the rollers 23 in the through grooves 22 of the carrier 21 will roll along the incident inner surface of the corresponding grooves 22 with a change in the distance from the axis of attachment of the rollers 23 on the rims 19 to the axis of rotation of the hubs 20 by the amount of doubled eccentricity.

The fastening of the roller 23 on the rim 19 is performed ahead of the rotation axis relative to the axis of attachment to the rim 19 of the crank 10 by an angle of 90 degrees, as well as less or more than this value. The choice of the lead angle is due to the need for a relative decrease in the speed of the stroke at its finish (when leading by an angle less than 90 degrees), or a relative increase in the speed of the stroke at its finish (when ahead of the corner greater than 90 degrees).

Instead of the roller 23 inside the through groove 22 of each of the carrier 21, it is possible to install a slider which, through the rolling bearing, is mounted on a finger pressed into the end of the corresponding rim 19.

From the outer ends of the rims 19 are attached protective casings 24 adjacent to the cranks 10 and rotating together with the corresponding rims 19.

In another embodiment, the rocking machine along the outer diameter of each of the hubs 20 is made an annular groove in which the pulling rope 25 is laid. At one end, the pulling rope 25 is pivotally attached to the outer surface of the hub 20, and the other end is connected by a hinge 26 to the corresponding rim 19. Fastening the hinge 26 on the rim 19 is performed in advance in the direction of rotation relative to the axis of attachment to the rim 19 of the crank 10 by an angle of 90 degrees, as well as less or more than this value. The choice of the lead angle is due to the need for a relative decrease in the speed of the stroke at its finish (when leading by an angle less than 90 degrees), or a relative increase in the speed of the stroke at its finish (when ahead of the corner greater than 90 degrees).

Figure 4 illustrates a graphical dependence of the change in the rotational speed n _{var of the} rim 19 and the distance R _var from the positioning point of the roller 23 mounted on the end of the rim 19, inside the through radial groove 22 of the carrier 21 attached to the hub 20, to the axis of rotation of the latter mounted on the output gear shaft 11. Moreover, the graphical dependence 1 is sinusoidal and is obtained by projecting on the time axis t the radius vector r, performing a clockwise rotation, forming a circle. The value of the radius vector r is equal to the difference between the maximum R _{var max} and the minimum R _{var min} distances from the positioning point of the roller 22 to the axis of rotation of the hub 20, which corresponds to the eccentricity e, being simultaneously the amplitude A of the graphical dependence considered:

r = e = A = R _{var max} - R _{var min}

At the same time (Fig. 5), the speed V _{var of the} vertical reciprocating movement of the cable suspension 5 with the wellhead rod 6 in time t during the rotational movement of the rim 19 changes according to the same sinusoidal law, changing its direction twice twice for each cycle swing rocker 3.

On the cycle of figures 6-10 presents schemes of sequential rotation of 360 degrees of the rim 19 and, accordingly, the full cycle (working stroke up and idle down) of the reciprocating movement of the wellhead rod 6 in the well. Moreover, during the clockwise rotation of the hub 20, the carrier 21 mounted on it by means of a roller 23 moving in its through groove 22, pivotally mounted on the end face of the rim 19, transmits torque to the rim 19. The crank 10 rigidly connected to the rim 19 by means of a connecting rod 8 sets swinging to the balancer 3, through the head 4 of which the cable suspension 5 with the wellhead rod 6 fixed at its end is transmitted reciprocating.

When the rim 19 is rotated clockwise, the axis of the hub 20 is shifted by the eccentricity e horizontally in the direction opposite to the head 4 of the balancer 3, relative to the axis of rotation of the rim 19. The latter rotates in the same direction as the hub 20, due to this eccentricity with variable frequency n _var . Moreover, the minimum rotation speed n _{var min of the} rim 19 together with the crank 10 (see Fig.6) takes place at a minimum distance R _{var min} from the axis of rotation of the hub 20 to the axis of attachment to the rim 19 of the roller 23. With this arrangement, the crank 10, connecting rod 8 and the balancer 3 with the head 4 give a minimum speed V _{var min} to the translational movement of the cable suspension 5 at the lower point of idle.

With further rotation of the rim 19 together with the crank 10 clockwise (see Fig. 7), the rotation speed n _{var of the} rim 19 smoothly starts to increase according to the sinusoidal law with increasing distance R _var from the axis of rotation of the hub 20 to the axis of attachment to the rim 19 of the roller 23 , which also leads to an increase in the speed V _{var of the} translational movement of the cable suspension 5 upward according to a smooth sinusoidal law during the working stroke.

The subsequent rotation of the rim 19 together with the crank 10 (see Fig. 8) leads to a further increase in frequency to n _{var max} according to a sinusoidal law in proportion to the increase in the distance from the axis of rotation of the hub 20 to the axis of attachment on the rim 19 of the roller 23 to the maximum value of R _{var max} , which also leads to a further smooth increase in the speed V _{var of the} translational movement of the cable suspension 5 upward according to the sinusoidal law during the working stroke. It is in this position, when the crank 10 and the connecting rod 8 take a vertical position when the crank 10 is at the lowest point, the head 4 of the balancer 3 together with the cable suspension 5 will rise to the highest point, thus completing the stroke. At the indicated highest point, a reverse occurs, and the forward movement of the cable suspension 5 downward begins with a decrease in the speed V _var according to the sinusoidal law.

Further rotation of the rim 19 together with the crank 10 (see Fig. 9) continues to lead to a decrease in the frequency n _var according to a sinusoidal law with a proportional decrease in the distance R _var from the axis of rotation of the hub 20 to the axis of attachment of the roller 23 with continued idling downward.

And finally, the rotational speed n _{var min of the} rim 19 together with the crank 10 (see Fig. 10) will take its minimum value according to a sinusoidal law with a corresponding reduction to the minimum value R _{var min of the} distance from the axis of rotation of the hub 20 to the axis of attachment to the rim 19 of the roller 23, which leads according to a sinusoidal law to achieve the minimum speed V _{var min of the} forward movement of the cable suspension 5. Moreover, in this position, when the connecting rod 8 and crank 10 take a vertical position when the crank 10 is at the highest point, the head 4 of the balancer 3 together with the cable suspension 5 will lower to the lowest point, thus completing the idling.

From this moment, the working stroke begins again, when the rotation of the rim 19 together with the crank 10 begins to occur with increasing frequency n _var smoothly according to the sinusoidal law with a gradual increase in the distance R _var from the axis of rotation of the hub 20 to the axis of attachment of the roller 23. The latter leads to a further smooth sinusoidally increase speed V _var translational movement suspension cable 5, but now up during the power stroke (see. Figure 10) until the maximum value (again see FIG. 6) and one complete qi la.

For the reverse rotation of the crank mechanism of the rocking machine (counterclockwise), the eccentricity e is reversed by shifting the axis of rotation of the output shaft of the gearbox towards the head of the balancer relative to the axis of rotation of the crank, moving the platform frame 14 along the supporting frame 1.

In order to further increase the rotational speed n _{var of the} rim 19 and the corresponding increase in the working speed V _{var of the} wellhead 6 when they are sinusoidally growing as a result of the above actions, the through groove 22 of the carrier 21 is inclined at a certain angle α with respect to the longitudinal axis of the carrier 21 (see 11 and 11a) in the direction of rotation. In this case, the roller 23, pivotally mounted on the end face of the rim 19, during the rotation of the hub 20 will transmit torque to the rim 19, rolling along the inner running surface of the through groove 22, as if by copying, while giving an additional increment to the rotational speed n _{var of the} rim 19. Moreover, the increment of the rotational speed n _{var of the} rim 19 will be the greater, the greater the angle of inclination of the OS will be set to the through groove 22.

If necessary, slow down the increase in the rotation speed n _{var of the} rim 19 with the crank 10 and the corresponding increase in the speed of the working stroke V _{var of the} cable suspension 5 at the end of the working stroke before reversing to idle, the through radial groove of carrier 21 at its end farthest from the axis of rotation of the hub 20 is bent some calculated value against the direction of rotation (see Fig. 12). When the hub 20 is rotated clockwise with the roller 23 rolling along the running inner surface of the through groove 22 of the carrier 21, the copy of the roller 23 will go deeper into the bend of the through groove 22 of the carrier 21, thereby ensuring some lag in the rotation of the rim 19 at the finish of the working stroke, thereby not less with an increase in its speed V _var (see Fig. 12a).

To reduce contact stresses along the line of contact of the outer diameter of the roller 23 with the running inner surface of the through groove 22 of the carrier 21, instead of the roller 23, a slider is inserted, which is inserted through the rolling bearing onto a finger pressed into the end of the rim 19 (see Figs. 13 and 13a). In this case, the slider is in contact with the running surface of the through groove 22 of the carrier 21 already along the entire lateral plane of the slider. In this case, the slider 13, pivotally mounted on a single finger 9, which, in turn, is pressed into the end face of the rim 6, during rotation of the hub 3 will transmit torque to the rim 19, sliding along the inner running surface of the through groove 22, as if by copy, and increasing the frequency of rotation n _{var of the} rim 19 according to the same principle as in Fig.6-10, or by giving an additional increment to the rotational speed of the rim 19, as in Fig.11-11a.

When using the “pulling” application of torque (FIGS. 14-22), in contrast to the above-mentioned “pushing” application of torque, during the uniform rotation of the hub 20, mounted on the output shaft of the gearbox (not shown) and shifted with an eccentricity e horizontally in the direction opposite to the location of the head 4 of the balancer 3 relative to the axis of rotation of the rim 19, rigidly connected to the crank 10, the latter, through a flexible connection in the form of a steel pulling rope 25 (or plate chain), atelnoe clockwise motion with variable frequency n _var. Moreover, the minimum rotational speed n _{var min of the} rim 19 together with the crank 10 is achieved at a minimum distance R _{var min} from the axis of rotation of the hub 20 to the pivot point 26 of the pulling rope 25 on the rim 19, and the crank 10, the connecting rod 8 and the balancer 3 with the head 4 attach minimum speed Vvar _min to the translational movement of the cable suspension 5 at the lower point of idle (see Fig. 14).

With further rotation of the rim 19 together with the crank 10 clockwise (see Fig. 15), the rotational speed n _{var of the} rim 19 smoothly begins to increase according to the sinusoidal law as the distance R _var from the axis of rotation of the hub 20 to the point of hinge 15 of the fastening of the steel pulling rope 14 on the rim 6, which also leads to an increase in the speed V _{var of the} translational movement of the cable suspension 5 upward according to a smooth sinusoidal law during the working stroke.

The subsequent rotation of the rim 19 together with the crank 10 (see FIGS. 15-18) leads to a further increase in the rotational speed n _{var of the} rim 19 according to a sinusoidal law in proportion to the increase in the distance R _var from the axis of rotation of the hub 20 to the point of articulation 26 of the fastening of the pulling rope 25 on the rim 19, which also leads to a further smooth increase in the speed V _{var of the} translational movement of the cable suspension 5 upward according to the sinusoidal law during the working stroke. It is in this position, when the crank 10 and the connecting rod 8 take a vertical position when the crank 10 is at its lowest point, the head 4 of the balancer 3 together with the cable suspension 5 will rise to the highest point, thus completing the stroke.

At the indicated highest point, a reverse occurs and the translational movement of the cable suspension 12 downward begins with a decrease in the speed V _var according to a sinusoidal law.

Further rotation of the rim 19 together with the crank 10 (see Fig. 19-22) continues to reduce its frequency n _var according to a sinusoidal law with a proportional decrease in the distance R _var from the axis of rotation of the hub 20 to the point of hinging 26 of the pulling rope 25 on the rim 19 with continued idle down.

And finally, the rotational speed of the rim 19 together with the crank 10 (see Fig. 22) will reach a minimum value of n _{var min} according to a sinusoidal law with a corresponding reduction in the distance from the axis of rotation of the hub 20 to the point of hinging 26 of the pulling rope 25 on the rim 19 to the minimum values of R _{var min} , which leads according to a sinusoidal law to reduce the speed of translational movement of the cable suspension 12 to the minimum value of V _{var min} . Moreover, in this position, when the crank 10 and the connecting rod 8 take a vertical position when the crank 10 is at its highest point, the head 4 of the balancer 3 together with the cable suspension 5 will lower to the lowest point, thus completing the idle stroke.

From this moment, the working stroke begins again, while the rotation of the rim 19 together with the crank 10 will occur with an increase in the frequency n _var smoothly according to a sinusoidal law with a further increase in the distance R _var from the axis of rotation of the hub 20 to the point of articulation 26 on the rim 20 of the pulling rope 25 that will lead to further smooth sinusoidally increase speed V _var translational movement suspension cable 5, but now up during the power stroke (see. Figure 14) until reaching a maximum value (see again. phi .22) and one complete cycle.

For clarity, tables 1-3 provide examples of the implementation of the proposed method of oil production in comparison with typical production modes using standard pumping units. Set the parameters (see Fig.6-10 and 14-22): the inner diameter of the rim 19 D _ext = 1800 mm; outer diameter of the hub 20 d _nap = 800 mm; hub speed 20 n = 10 rpm Then, with different values of the eccentricity e, the proposed method allows to obtain the following indicators:

Table 1 No. p / p Eccentricity e, mm The angle of rotation of the rim, degrees Variable radius R _var , mm Rim rotation frequency n _var , rpm The average rim rotation speed n _cp , rpm Rim rotation frequency n _var , rpm The average rim rotation speed n _cp , rpm one 0 500.00 10.00 6.00 2 45 678.89 13.58 8.15 3 90 984.89 19.70 11.82 four 135 1216.19 24.32 14.59 5 400 180 1300.00 26.00 18.00 15.60 10.75 6 225 1216.19 24.32 14.59 7 270 984.89 19.70 11.82 8 315 678.89 13.58 8.15 9 360 500.00 10.00 6.00

table 2 No. p / p Eccentricity e, mm The angle of rotation of the rim, degrees Variable radius R _var , mm Rim rotation frequency n _var , rpm The average frequency of rotation of the rim n _sr , rpm Rim rotation frequency n _var , rpm The average rim rotation speed n _cp , rpm one 0 600.00 10.00 7.00 2 45 719.84 12.00 8.40 3 90 948.68 14.38 10.07 four 135 1132.60 18.88 13.22 5 300 180 1,200.00 20.00 14.50 14.00 10.15 6 225 1132.60 18.88 13.22 7 270 948.68 14.38 10.07 8 315 719.84 12.00 8.40 9 360 600.00 10.00 7.00

Table 3 No. p / p Eccentricity e, mm The angle of rotation of the rim, degrees Variable radius R _var , mm Rim rotation frequency n _var , rpm The average rim rotation speed n _cp , rpm Rim rotation frequency n _var , rpm The average rim rotation speed n _cp , rpm one 0 700.00 10.00 8.00 2 45 771.65 12.86 10.29 3 90 921.95 13.17 10.54 four 135 1050,99 15.01 12.01 5 200 180 1,100.00 15.71 13.08 12.57 10.47 6 225 1050,99 15.01 12.01 7 270 921.95 13.17 10.54 8 315 771.65 12.86 10.29 9 360 700.00 10.00 8.00

As can be seen from Table 1, with an eccentricity e equal to 400 mm and a minimum rim rotation speed of 10 rpm, the average rpm of the rpm n _cp is 18 rpm, i.e. 1.8 times more. By setting the minimum rim rotation frequency equal to, for example, 6 rpm, we obtain the average rim rotation frequency n _cp; equal in this case to 10.75 rpm, also exceeding the minimum specified frequency for this case by 1.8 times. Consequently, the increase in oil production will be 80%.

From Table 2 it follows that with an eccentricity of e equal to 300 mm, the average rpm of the rim n _cp is 14.5 rpm. By setting the minimum rim speed not equal to 10 rpm, but say 7 rpm, we get the average rpm rotation speed n _cp of 10.15 rpm. As you can see, the average frequency for a full rim revolution exceeds the minimum frequency by 1.45 times.

Finally, with an eccentricity e of 200 mm (see Table 3), the average rpm of the rim n _cp is 12.86 rpm. When the minimum rim rotation speed is set to 8 rpm, the average rpm rotation speed n _cp will be 10.47, which is 1.3 times higher than the minimum.

The figures given in Tables 1-3 apply equally to devices using both a carrier and pulling ropes, as the ratio of the variable radii R _{var of the} hubs 20 and rims 19, as well as the rotational speeds n _{var, is the} same for both of these options, with the exception of an additional twist of the pulling rope to the hub.

The proposed rocking machine implements a method of oil production as follows.

According to the calculated average swing frequency n _{cp of the} balancer 3, set by the average rotational speed of the rims 19, the eccentricity e corresponding to the displacement of the platform frame 14 relative to the support frame 18 is calculated. The platform frame 14 is detached from the support frame 18, displaced, for example, by screw pair, the eccentricity e and again securely fastened with the same set of bolted connections.

Next, the wellhead rod 6 and the entire column of pump rods connected to the SHG plunger (not shown) are attached to the cable suspension 5. From this moment, the smooth start of the electric motor 13 through the V-belt drive 12 starts the gearbox 11. In this case, the output shaft of the gearbox 11 should rotate clockwise when the eccentricity is shifted to the right (see Fig.6) and counterclockwise when the eccentricity is shifted to the left (see figure 1) from the side of the observer.

Through the hubs 20, mounted on the ends of the output shaft of the gearbox 11, the torque is transmitted by the carriers 21 to the rollers 23 placed in the through grooves 22 and pivotally mounted on single fingers. In turn, single fingers pressed into the ends of the rims 19 transmit rotation to the rims 19. In the process of rotation of the rims 19, rigidly connected to the corresponding cranks 10, with the help of the connecting rods 8, the force is transmitted to the balancer 3 through the yoke 7, forcing it to make oscillating movements. The head 4 of the balancer 5 sets the reciprocating movement of the cable suspension 5 and, through the wellhead rod 6, then to the plunger SHGN.

The difference of the proposed group of inventions is that the oscillating movement of the balancer 5 is accelerated at the upper point of the head 4 of the balancer 5 and slowed down at the lower point of its location. Accordingly, the rope suspension 5 simultaneously reproduces the reciprocating movement that increases to the maximum

values of V _{var max} , then decreasing to the minimum value of V _{var min} according to a sinusoidal law.

It is especially necessary to note that, with a significant increase in the performance of USGN in general, due to an increase in the pumping frequency, special attention should be paid to the pump fill factor, for which, if necessary, it is necessary to use the suction and discharge valves of the SHGN pumps with increased flow cross-sections, which ensure efficient filling of production pumps.

Using the proposed method and device for its implementation allows you to:

- significantly increase (up to two or more times) the productivity of oil production using SHGN, further approximating this type of pumps by this indicator to high-performance electric centrifugal pumps (ESP);

- significantly speed up idling with its deceleration according to a sinusoidal law as it approaches the lower critical point, which further contributes to an increase in the filling factor of the plunger pump under pressure of the well column above the ShGN pump immersed in the well, since some deceleration at the idle finish gives additional time to fill the internal cavity of the pump above the plunger;

- reduce the negative impact of dynamic processes at the beginning of the upward stroke due to some calculated decrease in the speed of reciprocating motion at the lower point with compensation and a smooth increase in speed at the upper point according to the sinusoidal law;

- reduce leakage in the gap of the plunger pair with acceleration of the working stroke at steady-state dynamic mode, since the possibility of these leaks is reduced in time with the same length of the working stroke of the plunger.

Claims (8)

1. The method of oil production using a sucker rod pump, comprising changing the rotational speed of the crank of the rocking machine and coordinated with it through changing the angular velocity of the rocker balancer changing the speed of the reciprocating movement of the wellhead rod, characterized in that the rotational speed of the crank and the speed matched to it the reciprocating movement of the rod is changed according to a sinusoidal law, smoothly accelerating the working stroke at which the translational movement of the rod up reaches its maximum speed growth with the vertical position of the connecting rod and crank at the lower point, and proportionally slowing down the idle speed, in which the translational movement of the rod down reaches the minimum speed with the vertical position of the connecting rod and crank at the upper point, while reducing the speed of the rod at the beginning of the working stroke and at the end of idling by an amount less than the average speed of the reciprocating motion of the rod. 2. Rocking machine for oil production using a sucker rod pump, comprising a support frame, a stand on which a balancer is mounted using a hinge, having a head with a cable suspension and a wellhead on one side, and a hinged traverse with spaced apart on the other hand on both sides of the rack by connecting rods, each of which is connected to the crank on which the counterweight is mounted, and also containing a gearbox, the input shaft of which is connected via a V-belt transmission to an asynchronous electric motor, the fact that the cranks are mounted on rims that are mounted with the possibility of circular motion in the frame of roller bearings or roller bearings placed around the perimeters of windows made in vertical frames, which are fixed on opposite sides of the support frame, and the gearbox and electric motor are mounted on a platform frame mounted, in turn, on the support frame with the ability to move along the direction of the balancer, and at the ends of the output shaft of the gearbox in the plane of circular motion of the rims mounted hubs , the outer diameter of which is made smaller than the inner radius of the rims, while carriers are attached to the hubs, each of which has a through radial or inclined groove, inside which a roller is placed pivotally with a bearing on a finger, pressed into the end of the corresponding rim ahead of in the direction of rotation at an angle of 90 °, as well as less or more than this value, relative to the attachment point to the rim of the crank. 3. The rocking machine according to claim 2, characterized in that the through radial grooves of the carrier have smooth bends against the direction of rotation at the ends remote from the axis of rotation of the hub. 4. The rocking machine according to claim 2, characterized in that the through inclined grooves of the carrier are made with a deviation in the direction of rotation of the end of the groove remote from the axis of rotation of the hub. 5. The rocking machine according to one of claims 2 to 4, characterized in that the through grooves of the carrier are made curved, either in the form of an arc of a circle, or in the form of another smooth geometric dependence. 6. The rocking machine according to one of claims 2 to 4, characterized in that the through grooves of the carrier are made in the form of a combination of straight and curved sections. 7. The rocking machine according to claim 3 or 4, characterized in that instead of the roller, a slider is placed inside the through groove of each carrier, also inserted through a hinge (such as a rolling bearing) onto a finger pressed into the end of the corresponding rim. 8. A rocking machine for oil production using a sucker rod pump, comprising a support frame, a stand on which a balancer is mounted using a hinge, having a head with a cable suspension and a wellhead on one side, and a hinged traverse with spaced apart on both sides of the traverse with connecting rods connected to the crank on which the counterweight is mounted, and also containing a gearbox, the input shaft of which is connected to the electric motor by means of a V-belt transmission, characterized in that the crank mounted on rims that are mounted with the possibility of circular motion in the frame of rollers or roller bearings placed around the perimeters of windows made in vertical frames that are rigidly attached to opposite sides of the support frame, the gearbox and electric motor are rigidly fixed to the platform frame installed in in turn, on the support frame with the ability to move along the direction of the balancer, and at the ends of the output shaft of the gearbox in the plane of the circular motion of the rims, hubs are mounted, the outer diameter tr of which is made smaller than the inner radius of the rims, while an outer groove is made in the outer diameter of each of the hubs, into which a pulling rope is laid, pivotally attached to the hub at one end, and also connected to the corresponding rim with a hinge mounted ahead of rotation in an angle of 90 °, as well as less or more than this value, relative to the attachment point to the crank rim, in addition, the pulling ropes laid in the annular grooves of the hubs must be pre-screwed onto the hubs and a value that ensures uniform load transfer along the arc of coverage of the outer diameters of the hubs during the tension process, but not exceeding the full perimeter of the outer circumference of the hub, in order to exclude the winding of each rope itself during each complete revolution relative to its own axis of rotation, and the radius of the groove the cross-sectional grooves on the hubs must correspond to the radius of the pulling rope with the necessary clearance for unimpeded laying and tight fit to the groove, which ensures gradual redistribution of load along the arc of contact.

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