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

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

 

The invention relates to the field of the oil industry and can be used in the operation of wells sucker rod pumps (SRP system) reciprocating using the drive pumping units, allowing to improve the performance of oil well pumping units (SSNU) to change the speed up or down within each cycle of oscillation of the wellhead of a stock suspension of the column rod connected to the plunger of SRPS.

The known method of operation of wells plunger depth pumps capable of non-linear speed up and down wellhead rod pumping unit within one cycle of oscillation (see Vnewnostj, Vigerie, Say, Uscasino, Sci. Borehole pumping units for oil extraction. M: sue Izd-vo "Oil and gas state oil and gas University. University, 2002 [1]).

The disadvantage of this method is the lack of alignment with the specific law changes nonlinear speed lifting / lowering wellhead rod pumping unit and the duration of each cycle of the swing.

Known machine-rocking with the drive Mark II (see [1])with desexualises mechanism, in order to increase the "pull" lever system traverse pumping unit located in front of the gearbox, near the head of the balancer, and CCA is the second design of the crank and its location allows to modify the application of the moment created by the crank in relation to the moment created weight of the sucker rods string.

This device is inherent in the above disadvantages, which limit the performance of oil production and the motivation of producers to a wider application of the sucker rod pump with machines-rockers the drive.

Closest to the invention in the part of the method is the operation of wells with plunger depth pumps company "Lufkin" (see [1]), in which the running time of the wellhead rod up increased by lowering the acceleration at the beginning of turn up. This solution allows to reduce the overload on the drive and the pump rod in the most intense period of the cycle, which is the beginning of the turn up. The disadvantages of this method are:

a) lack of alignment with the specific law of diminishing acceleration at the beginning of turn up, as in the case of analogues;

b) reducing the performance of the pump unit due to the increase in the operating time up.

Closest to the invention a device is a machine-rocking with the asynchronous motor, which is controlled using control station WM triol 01 (see [1]). This drive provides smooth, stepless regulation of speed induction motor with capacity from 3 to 37 kW at 0 denominating values (1500 rpm) and as a result, nonlinear speed lifting / lowering rod.

The disadvantages of this device are:

(a) the limitations in changing the rotational speed of the motor during each cycle of the swing - up to 40%;

b) overloading and overheating of the induction motor as the deflection of the rotation frequency from the nominal value;

C) the above adverse conditions can cause vibration and premature equipment failure.

The objective of the invention is a method of oil extraction and pumping unit for its implementation without drawbacks and prototype.

The technical result achieved when 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 oil extraction method using SRPS, including changing the frequency of rotation of the crank pumping unit and agreed with him by changing the angular velocity of the swing of the balance wheel change speed of the reciprocating movement of the wellhead rod, under the proposal, the rotational speed of the crank, and agreed with her speed reciprocating motion of the wellhead stem change in a sinusoidal manner, smoothly accelerating stroke, in which the ongoing is the second movement of the rod to the upper reaches its maximum speed when the vertical position of the connecting rod and crank at the bottom, and proportional slowing idling, whereby forward movement of the rod down reaches the minimum speed when the vertical position of the connecting rod and crank at the upper point, and the speed of the stock at the beginning of the stroke and at the end of idling reduced by the amount, less the average speed of the reciprocating motion of the rod.

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

Changing the speed of movement of the crank and wellhead rod sinusoidal significantly, but slowly, in a sinusoidal dependence, increase the speed of the stroke to values that do not harm the dynamics of the whole process, with a consequent reduction in speed at idle down on the same sinusoidal dependence. The result is significant (up to two times or more) exceeding the average frequency of rotation of the crank and, accordingly, the average speed of the reciprocating movement of the piston rod of the cable suspension relative to typical values of these quantities on traditional technologies. In addition, achieved a significant reduction in congestion on the pump rod and the actuator as a whole, which take place at the end of the idling down and at the beginning of the stroke up is when using traditional technologies.

Reducing the speed of movement of the RAM at the beginning of the stroke up and at the end of the idle speed down to less average speed reciprocating motion, reduces adverse dynamic loads, thus providing a higher performance compared to the prototype. It happens this way. At the beginning of the stroke, when the piston rod of the cable suspension begins its upward movement, the plunger of the pump at the bottom of the column rod continues for some time to move downward due to its own weight and inertia of motion of the entire weight of the pumping Stanger creating cyclical peak dynamic load smoothing which can effectively implement the proposed method for reducing (to the extent specified above) the speed at the completion of idling and at the beginning of the stroke at the bottom of the location of the rod. This speed reduction shaft is fully compensated by the acceleration at a smooth increase in speed up the sine law with an already established dynamics.

Technically the solution of this problem is realized by introducing into the kinematics of a typical pumping unit additional link that provides the offset of the axis of rotation of the output shaft of the gearbox relative to the axis of rotation of the crank. The specified offset is forms of eccentricity, the change in the value which causes the change of rotation speed of the crank and the associated speed of the reciprocating movement of the wellhead Assembly. Accordingly, with the increase of the eccentricity increases, the oscillation frequency of the balance-wheel, and, as a consequence, the overall performance of the installation as a whole. In the proposed invention, the additional element can be performed in two variants: in the "pushing" the application of torque by installing a hard link in the form of carrier and roller, hinged to the edge of the rim, as well as in the "pull" application of torque with the installation of the flexible element in the form of a pull rope.

The technical result is achieved by the fact that the pumping unit for oil extraction using sucker rod pump, comprising a support frame, a rack on which the use of the hinge is mounted rocker having, on the one hand, the cylinder with rope suspension and estuarine stock, and, on the other hand, is pivotally suspended from the yoke with spaced on both sides of the rack rods, each of which is connected to the crank, which is attached to the counterweight, and the gearbox input shaft by V-belt transmission is connected with an induction motor, according to the invention cranks mounted on rims that installed with possibly the TEW circular motion in the frame of a roller supports (or roller bearings), located at the perimeters of the Windows, made in the vertical frames, which are fixed on opposite sides of the base frame, and a gear and a motor mounted on the frame platform installed in the support frame can move along the direction of the balancer, and at the ends of the output shaft of the gearbox in the plane of circular motion rims mounted hub, the outer diameter is made smaller inner radius rims, the hubs are attached to the carrier, each of which has a through radial or oblique groove within which is placed a roller mounted hinge (with bearing) on the finger is pressed into the end of the corresponding rim with ahead in the direction of rotation at an angle of 90 degrees, and less or more than this value, relative to the axis of attachment to the rim of the crank.

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

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

Through the slots drove made curved or in the form of an arc of a circle, or other smooth geometric dependencies.

Through the slots drove made in the form of a combination of straight and crooked the line sections.

Inside the through groove of each of the led instead of the roller can be placed crawler mounted via a hinge (e.g., bearing) on the finger is pressed into the end of the corresponding rim.

The technical result is also achieved by the fact that in the pumping unit for oil extraction using sucker rod pump, comprising a support frame, a rack on which the use of the hinge is mounted rocker having, on the one hand, the cylinder with rope suspension and estuarine stock, and, on the other hand, is pivotally suspended from the yoke with spaced on both sides of the beam connecting rods connected to the crank, which is attached to the counterweight, and the gearbox input shaft by V-belt transmission is connected with an electric motor, according to the invention cranks mounted on rims that are installed with the possibility circular motion in the frame of the roller or roller bearings)placed at the perimeters of the Windows, made in the vertical frames, which are rigidly attached to opposite sides of the base frame, and the gearbox and the motor is rigidly mounted on the frame platform mounted on a support frame can move along the direction of the balancer, and at the ends of the output shaft of the gearbox in the plane of circular motion rims mounted hub, N. the outer diameter is made smaller inner radius rims thus the outer diameter of each of the hubs made circular groove, in which is laid a pull rope, one end pivotally attached to the hub, and the other end connected with the corresponding rim also hinge set ahead in the direction of rotation at an angle of 90 degrees, and less or more than this value, relative to the point of attachment to the rim of the crank.

Pulling the ropes, arranged in the annular groove of the respective hubs, pre-screw on the hub by an amount providing a uniform transfer of load along the arc of coverage of the outer diameters of the hubs in the tensioning process, but not exceeding the total perimeter of the outer circumference of the hub.

The radii of the annular grooves in its cross-section, made according to the outer diameter of each of the hubs correspond to the radii of the pulling ropes with the necessary clearance for easy installation and a snug fit to the gutter.

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

The addition of the device, on the one hand, rims, mounted rotatably in the frame of a roller supports (or roller bearings)placed at the perimeters of the Windows, made in the vertical frames that are tightly priciple who are from opposite sides to which are fixed on the piles supporting frame, with the fixation on the rims cranks, and on the other hand, the mounting of the gearbox on the frame platform mounted for movement on the base frame along the equaliser, with simultaneous installation on the ends of the output shaft of the gearbox hub provides the ability to offset the axes of rotation of these hubs relative to the axis of rotation of the cranks. Thus is formed the eccentricity, which allows, by changing the frequency of oscillations of the balance wheel, to change the overall performance usgn.

The addition of the device measured including carriers, secured to the hub or, alternatively, pulling the ropes ensures the rotation of the rims with the frequency variable sinusoidal.

Condition ahead in the direction of rotation of the attachment point to a pair of the rims of the finger, which is pivotally fixed the video posted in the radial through groove was taken (or, alternatively, the point of hinged attachment of the pull rope with the rim), with respect to an axis of the mounting on the corresponding rim of the crank, provides a relative decline in the speed of the stroke at the finish line when ahead at an angle less 90 degrees, and correspondingly increase the speed of the stroke at the finish line when ahead at more than a right angle of 90 degrees.

Running through the radial grooves drove with smooth sigibert direction of rotation remote from the axis of the hub end allows to reduce the speed of the stroke of the wellhead stock at the finish of the stroke and the corresponding smooth decrease of the frequency of rotation of the rim even at the approach head balancer to its highest point of the swing.

Execution slanted through the slots were taken with deviation as the distance from the axis of the hub in the direction of rotation makes it possible to increase the average frequency of rotation of the rim relative to the hub and thereby improve the performance of oil production.

Performing the pass-through slots drove curved or in the form of an arc of a circle, or other smooth geometric dependence, or as a combination of rectilinear and curvilinear sections can further improve the dynamics of the swing.

Run inside through (both radial and oblique) of the groove of each of the led instead of the roller screw mounted through a hinge (e.g., bearing) on the finger is pressed into the end of the corresponding rim, allows to reduce the contact stresses, since the slider makes sliding all its adjacent lateral surface by rolling the inner surface of the through groove drove in the transmission of torque.

Pulling the ropes, arranged in the annular groove of the hub, pre-screw on the hub by an amount providing a uniform transfer of load along the arc of coverage of the outer diameters of the hubs in the tensioning process, but not exceeding the full outer perimeter of OCD is gnosti hub, in order to exclude each winding of the rope on itself during each full rotation about its own axis of rotation. In addition, the radius of the grooves grooves on the hub cross-section must correspond to the radius of the pull rope with the necessary clearance for easy installation and a snug fit to the groove that provides a smooth distribution of the load over the arc of contact.

Listed distinguishing characteristics are not known in methods of production with the use of sucker rod pumps and pumping units for their implementation.

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

figure 1 is a side view of the pumping unit with offset 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 with the crank in the direction of the head of the balancer on the value of eccentricity e (use case was taken);

figure 2 is a side view of the pumping unit with offset hub mounted on the output shaft of the gearbox, on the rim rigidly connected with the crank in the direction of the head of the balancer on the value of eccentricity e (variant of use of the traction rope);

figure 3 - rear view of a pumping unit (option use traction rope);

figure 4 - graphical C the dependence changes with time t of the rotation frequency n varclockwise rim and distances Rvarfrom the point of attachment to the rim of the roller receiving torque from the carrier (or of the traction rope) to the axis of rotation of the hub;

figure 5 - graphical dependency changes over time t with velocity Vvarreciprocating movement of the cable hangers with wellhead rod and frequency of the clockwise rotation of the rim nvar;

figure 6 - arrangement is installed on the rim of the roller, is placed inside the through radial groove was taken at a minimum distance of Rvar minfrom the roller axis to the axis of rotation of the hub and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according to Fig.6;

figure 7 - arrangement is installed on the rim of the roller, is placed inside the through radial groove drove by rotating the rim clockwise by 90 degrees relative to the location of figure 6 and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according to Fig.7;

on Fig - arrangement is installed on the rim of the roller, is placed inside the through radial groove drove by rotating the rim clockwise is clockwise 180 degrees relative to the location of figure 6, at which distance from the roller axis to the axis of rotation of the hub has a maximum value of Rvarmaxand the corresponding location of the balancer with the cylinder, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according Fig;

figure 9 - layout is installed on the rim of the roller, is placed inside the through radial groove drove attached to the hub by rotating the rim clockwise 270 degrees relative to the location of figure 6 and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according to figure 9;

figure 10 - location scheme is installed on the rim of the roller, is placed inside the through radial groove drove by rotating the rim clockwise 360 degrees relative to the location of figure 6 and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according to figure 10;

figure 11 - location scheme is installed on the rim of the roller, is placed inside the through the inclined groove drove attached to the hub, with a minimum distance of Rvar minfrom the roller axis to the axis of brasiliatopical; on figa - arrangement is installed on the rim of the roller, is placed inside the through inclined slots were taken by rotating the rim clockwise 180 degrees, at which the distance from the roller axis to the axis of rotation of the hub has a maximum value of Rvar max;

on Fig - arrangement is installed on the rim of the roller, is placed inside the through radial groove drove with his smooth bend in the direction,

opposite to rotation, with a minimum distance Rvarminfrom the roller axis to the axis of rotation of the hub; figa - arrangement is installed on the rim of the roller, is placed inside the through radial groove drove with his smooth bend in the direction opposite to the rotation by rotating the rim clockwise 180 degrees, at which the distance from the roller axis to the axis of rotation of the hub has a maximum value of Rvarmax;

on Fig - arrangement is installed on the rim of the slide located inside the through the inclined groove was taken at a minimum distance of Rvar minfrom the axis of the slide to the axis of rotation of the hub; figa - arrangement is installed on the rim of the slide located inside the through radial groove drove by rotating the rim clockwise 180 degrees, at which the distance from the axis of the slide to the axis of rotation of the hub to them is no maximum value Rvar max;

on Fig - arrangement of the hinge connection of the pull rope on the rim when the minimum distances Rvar minfrom the swivel to the axis of rotation of the hub and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according Fig;

on Fig - arrangement of the hinge connection of the pull rope on the rim during rotation of the rim clockwise by 45 degrees relative to Fig and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according Fig;

on Fig - arrangement of the hinge connection of the pull rope on the rim during rotation of the rim clockwise by 90 degrees relative to Fig, and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according Fig;

on Fig - arrangement of the hinge connection of the pull rope on the rim during rotation of the rim clockwise by 135 degrees relative to Fig and the relative position of the rocker-head, connecting rod and crank; figa is a graph showing the change of frequency of rotation about the n varin time t, when positioned according Fig;

on Fig - arrangement of the hinge connection of the pull rope on the rim during rotation of the rim clockwise 180 degrees relative to Fig and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according Fig;

on Fig - arrangement of the hinge connection of the pull rope on the rim during rotation of the rim clockwise 225 degrees relative to Fig and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according Fig;

on Fig - arrangement of the hinge connection of the pull rope on the rim during rotation of the rim clockwise 270 degrees relative to Fig and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according Fig;

on Fig - arrangement of the hinge connection of the pull rope on the rim during rotation of the rim clockwise 315 degrees relative to Fig and the relative position of the rocker-head, connecting rod and crank; figa - graph is modify the frequency of rotation of the rim n varin time t, when positioned according Fig;

on Fig - arrangement of the hinge connection of the pull rope on the rim during rotation of the rim clockwise 360 degrees relative to Fig and the relative position of the rocker-head, connecting rod and crank; figa is a diagram showing changes in the rotational speed of the rim nvarin time t, when positioned according Fig.

The proposed machine-rocking (see figure 1, 2, 3) includes a support frame 1, on which is rigidly fixed hour 2. Top rack 2 pivotally mounted rocker 3. On one end of the rocker 3 set head 4, to which is attached the cable suspension with 5 wellhead rod 6. On the opposite end of the rocker 3 articulated through the medium of the bar 7 is connected with the connecting rods 8, which are spaced on either side of the rack 2. In turn, each of the connecting rod 8 is connected with the cranks 10, on which are mounted with the possibility of relative displacement of the counterweight 9.

The input shaft 11 through V-belt transmission 12 is connected to the asynchronous motor 13, which drives the machine-rocking through the above-mentioned nodes and transmission mechanisms. The gear 11 and the electric motor 13 is rigidly mounted on the frame platform 14, which is installed on the base frame 1 can be moved along the direction of the balancer 3. FIC is the key of the relative displacement of the movable frame platform 14 along the support frame 1 when installing the calculated values for the eccentricity e is carried out using a positioning bar 15 with the fingers using the setup 16 with subsequent bolting the frame platform 14 to the base frame 1.

To the base frame 1 is rigidly mounted two spaced apart on either side of the gear 11 of the vertical frame 17 made them round Windows, the perimeter of which is placed a roller bearing 18. In window vertical RAM 17 for rotation in the frame of the roller bearings 18 mounted rims 19 ensuring alignment rims between itself and the location of the axes of the rims in the same plane with the axis of the swivel rocker 3 with rods 8.

The rim 19 is rigidly attached to the cranks 10, which in the model the pumping unit mounted on the output shaft directly. In the proposed as the pumping unit on the output shaft 11, on opposite ends of the shaft mounted to the hub 20, the outer diameter is made smaller inner radius rims 19 and which rotate in the plane of the circular movement of the respective rims.

In the proposed the pumping unit provides two options for providing additional eccentricity link: push ("hard"), installation of led and pulling (flexible) installation of the pull rope.

Thus, under option pushing additional link to the ends of the hubs 20 are attached to the carrier 21, each of which has a through groove 22. Through the slots 22 can be made to the difference is Noah configuration: radial; radial with a smooth bend against the direction of rotation remote from the axis of the hub 20 end; oblique deviation of the direction of rotation of the end of the groove 22, remote from the axis of rotation of the hub 20; curved or in the form of an arc of a circle, or other smooth geometric dependence; in the form of a combination of rectilinear and curvilinear sections.

Inside each of the through grooves 22 is a roller 23 mounted through a hinge (e.g., bearing) on the finger firmly pressed into the end of the corresponding rim 19. And to begin through the slots 22 have on the distance from the axis of rotation of the hub 20, the smaller the difference between the radius of the axis of the fixing single finger on the rim 19 with regard to the outer radius of the roller 23 and maximum eccentricity, and come to an end at a distance from the axis of rotation of the hub 20, the larger the amount of the radius of the axis of the fixing single finger on the rim 19 with regard to the outer radius of the roller 23 and maximum eccentricity. When the rollers 23 through the slots 22 of the carrier 21 will make rolling by rolling the inner surface of the respective grooves 22 with the change of the distance from the axis of the fixing rollers 23 on the rim 19 to the axis of rotation of the hub 20 by the value of the double eccentricity.

The fixing roller 23 on the rim 19 of perform ahead in the direction of rotation carries the flax axis of attachment to the rim 19 of the crank 10 at an angle of 90 degrees, as well as less or more than this value. The choice of values of the advance angle due to the need for the relative decrease the speed of the stroke at the finish line (when ahead at an angle less 90 degrees), or the relative speed of the stroke at the finish line (when ahead at more than a right angle of 90 degrees).

Instead of the roller 23 on the inside of the through groove 22 of each of the led 21 a possible installation of the slide, through which the rolling bearing mounted on the finger is pressed into the end of the corresponding rim 19.

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

In another embodiment of the pumping unit on the outer diameter of each of the hubs 20 are made circular groove, in which is laid pulling the rope 25. One end of the pulling rope 25 pivotally attached to the outer surface of the hub 20 and the other end is connected by a hinge 26 with the corresponding rim 19. The attachment hinge 26 on the rim 19 of perform ahead in the direction of rotation about the axis of attachment to the rim 19 of the crank 10 at an angle of 90 degrees, and less or more than this value. The choice of values of the advance angle due to the need for the relative decrease the speed of the stroke at the finish line (when ahead at an angle less 90 degrees), or relative to the positive speed of the stroke at the finish line (when ahead on the corner, more 90 degrees).

Figure 4 illustrates the graphical dependence of the rotation frequency nvarthe rim 19 and the distance Rvarfrom the point of positioning of the roller 23 mounted on the end face of the rim 19, inside the through radial groove 22 of the carrier 21, is attached to the hub 20 to the axis of rotation of the latter mounted on the output shaft of the gearbox 11. Moreover, the graphical dependence 1 is sinusoidal and obtained by projection on the time axis t of the radius-vector r, performs a rotational movement in a clockwise direction, forming a circle. Thus the value of the radius-vector r is equal to the difference between the maximum Rvar maxand minimum Rvar minthe distances from the point of positioning of the roller 22 to the axis of rotation of the hub 20, which corresponds to the eccentricity e, being both amplitude And consider graphical dependencies:

r=e=A= Rvar max- Rvar min

At the same time (figure 5), the velocity Vvarvertical reciprocating movement of the cable hangers 5 wellhead rod 6 in time t during the rotational movement of the rim 19 is changed by the same sine law, changing its direction to the opposite twice for each cycle of oscillation of the rocker 3.

On cycle figures 6-10 presents the schematic of a series of 360 degrees of rotation of the rim 19 and, accordingly, the floor is th cycle (stroke up and idle down) reciprocating movement of the wellhead rod 6 in the well. During clockwise rotation of the hub 20 is fixed on it took 21 by moving it through the slot 22 of the roller 23, a hinge mounted on the edge of the rim 19, transmits torque to the rim 19. Rigidly connected with the rim 19 of the crank 10 by means of a rod 8 specifies the swing of the balance wheel 3, through the head 4 which cable suspension 5 is fixed at its end estuarine shaft 6 is transmitted to the reciprocating movement.

During rotation of the rim 19 in clockwise rotation axis of the hub 20 is shifted by the amount of eccentricity e horizontally in the direction opposite the head 4 of the walking beam 3 relative to the axis of rotation of the rim 19. The latter rotates in the same direction as the hub 20, with thanks to the eccentricity of the variable frequency nvar. Moreover, the minimum frequency of rotation nvar minthe rim 19 in conjunction with the crank 10 (see Fig.6) is at a minimum distance of Rvar minfrom the axis of rotation of the hub 20 to the axis of the mounting on the rim 19 of the roller 23. With this arrangement, the crank 10, the connecting rod 8 and the collector head 3 head 4 gives the minimum velocity Vvar minthe translational motion of the suspension 5 at the bottom of idling.

Upon further rotation of the rim 19 together with the crank arm 10 clockwise (see Fig.7) engine speed nvarthe rim 19 is connecting to the sinusoidal begins to increase with increasing distance R varfrom the axis of rotation of the hub 20 to the axis of the mounting on the rim 19 of the roller 23, which also leads to the increase of the velocity Vvarthe translational motion of the cable suspension 5 up smooth sinusoidal during the stroke.

Subsequent rotation of the rim 19 in conjunction with the crank 10 (see Fig) leads to a further increase in the frequency to nvar maxsinusoidal proportion to the increasing distance from the axis of rotation of the hub 20 to the axis of the mounting on the rim 19 of the roller 23 to the maximum values of Rvar maxthat also leads to a further gradual increase in the velocity Vvarthe translational motion of the cable suspension 5 up sine law during the stroke. It is in this position when the crank 10 and the rod 8 will take a vertical position when the crank 10 at the lowest point, the head 4 of the rocker 3 in conjunction with the cable suspension 5 rises to the highest point, thus completing the stroke. In the specified highest point is the reverse, and starts the forward motion of the suspension 5 down with decreasing velocity Vvarsinusoidal.

Further rotation of the rim 19 in conjunction with the crank 10 (see Fig.9) continues to reduce the frequency of nvarsinusoidal with a proportional decrease of the distance Rvarfrom the axis of rotation of the hub 20 to the axis of the fixing roller 23 when the ongoing idle down.

Finally, the rotational speed of nvar minthe rim 19 in conjunction with the crank 10 (see figure 10) takes its minimum value in a sinusoidal manner with a corresponding decrease to the minimum value of Rvar minthe distance from the axis of rotation of the hub 20 to the axis of the fastening to the rim 19 of the roller 23, which results in a sinusoidal manner to achieve the minimum speed Vvar minthe translational motion of the cable suspension 5. And it is in this position, when the rod 8 and the crank 10 will take a vertical position when the crank 10 at the highest point, the head 4 of the rocker 3 in conjunction with the cable suspension 5 will drop to the lowest point, thus completing the idling.

From that moment again starts working stroke, when the rotation of the rim 19 in conjunction with the crank 10 begins to occur with increasing frequency, nvarsmooth sinusoidal with a gradual increase of the distance Rvarfrom the axis of rotation of the hub 20 to the axis of the fixing roller 23. The latter leads to further smooth sinusoidal speed Vvarthe translational motion of the cable hangers 5, but now up during the stroke (see figure 10) until reaching the maximum value (again, see Fig.6) and one complete cycle.

For reverse rotation of the crank mechanism with the ANCA-rocking (counterclockwise) direction of the eccentricity e is changed to the opposite, by shifting the axis of rotation of the output shaft of the gearbox towards the head of the rocker relative to the axis of rotation of the crank, moving frame platform 14 to the base frame 1.

With the purpose of further increasing the frequency of rotation nvarthe rim 19 and a corresponding increase in the speed of the stroke of the Vvarwellhead rod 6 when the sinusoidal growth as a result of the above actions through the groove 22 of the carrier 21 perform inclined at an angle α relative to the longitudinal axis of the carrier 21 (see 11 and 11a) in the direction of rotation. In this case, the roller 23, a hinge mounted on the edge of the rim 19, during rotation of the hub 20 will transmit torque to the rim 19, rolling on the inner rolling surface of the through groove 22, as the copier, thus giving additional increment of rotational speed of nvarthe rim 19. Moreover, the increment of the rotation speed nvarthe rim 19 is the greater, the greater the angle of OS can be specified through the slot 22.

If necessary to slow the growth of frequency of rotation nvarthe rim 19 with a crank 10 and the corresponding increase in the speed of the stroke of the Vvarcable hangers 5 at the finish of the stroke before the reverse idling through the radial groove of the carrier 21 in its farthest from the axis of rotation of the hub 20 the end of the bend on some calculated value against the direction of rotation (see Fig). During the rotation of the hub 20 in a clockwise direction by rolling the roller 23 on internal incident is poverhnosti through groove 22 of the carrier 21 as the Cam roller 23 delve into the bend of the through groove 22 of the carrier 21, thus, some delay in the rotation of the rim 19 at the finish of the stroke carried out however with the increase of its velocity Vvar(see figa).

To reduce the contact stresses at the contact line of the outer diameter of the roller 23 with the rolling of the inner surface of the through groove 22 of the carrier 21 instead of the roller 23 installing the slide, which is placed after bearing on the finger is pressed into the end face of the rim 19 (see Fig and 13A). When the slider is in contact with the rolling surface of the through groove 22 of the carrier 21 is already across the lateral plane of the slide. When the slider 13 is pivotally fixed on a single finger 9, 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 on the inner rolling surface of the through groove 22, as the copier, and increasing the frequency of rotation nvarthe rim 19 on the same principle as in Fig.6-10, or giving additional increment the frequency of rotation of the rim 19 as figure 11-11a.

When using "pull" applications torque (Fig-22), in contrast to the above mode "push" application of torque during uniform rotation of the hub 20 mounted on the output shaft of the gearbox (not shown) and shifted with eccentricity e horizontally with the horon, the opposite location of the head 4 of the walking beam 3 relative to the axis of rotation of the rim 19, rigidly connected with the crank 10, the latter, by means of a flexible connection in the form of a steel pull rope 25 (or plate chains), come into rotational motion clockwise with variable frequency nvar. Moreover, the minimum frequency of rotation nvar minthe rim 19 in conjunction with the crank 10 is achieved with a minimum distance of Rvar minfrom the axis of rotation of the hub 20 to the point of the hinged end 26 of the pull rope 25 on the rim 19 and the crank 10, the connecting rod 8 and the collector head 3 head 4 gives the minimum speed Vvarminthe translational motion of the suspension 5 at the bottom of idling (see Fig).

Upon further rotation of the rim 19 together with the crank arm 10 clockwise (see Fig) engine speed nvarthe rim 19 is smoothly sinusoidal begins to increase with increasing distance Rvarfrom the axis of rotation of the hub 20 to the hinge point 15 of the fastening steel pull rope 14 on the rim 6, which also leads to the increase of the velocity Vvarthe translational motion of the cable suspension 5 up smooth sinusoidal during the stroke.

Subsequent rotation of the rim 19 in conjunction with the crank 10 (see Fig-18) leads to a further increase in the frequency of rotation nvar the rim 19 of the sinusoidal proportion to the increasing distance Rvarfrom the axis of rotation of the hub 20 to the hinge point 26 fastening the pull rope 25 on the rim 19, which also leads to a further gradual increase in the velocity Vvarthe translational motion of the cable suspension 5 up sine law during the stroke. It is in this position when the crank 10 and the rod 8 will take a vertical position when the crank 10 at its lowest point, the head 4 of the rocker 3 in conjunction with the cable suspension 5 rises to the highest point, thus completing the stroke.

In the specified highest point of the reversal and starts the forward motion of the suspension 12 down with decreasing velocity Vvarsinusoidal.

Further rotation of the rim 19 in conjunction with the crank 10 (see Fig-22)continues to reduce its frequency nvarsinusoidal with a proportional reduction of the distance Rvarfrom the axis of rotation of the hub 20 to the point of the hinged end 26 of the pull rope 25 on the rim 19 at the ongoing idle down.

Finally, the frequency of rotation of the rim 19 in conjunction with the crank 10 (see Fig) attains the minimum value of nvar minin a sinusoidal manner with a corresponding decrease in distance from the axis of rotation of the foot is s 20 to the point of the hinged end 26 of the pull rope 25 on the rim 19 to the minimum value of R var minthat results in a sinusoidal manner to decrease the speed of the translational movement of the cable suspension 12 to the minimum value of Vvar min. And it is in this position when the crank 10 and the rod 8 will take a vertical position when the crank 10 at its highest point, the head 4 of the rocker 3 in conjunction with the cable suspension 5 will drop to the lowest point, thus completing the idling.

From that moment again starts working stroke, the rotation of the rim 19 in conjunction with the crank 10 will occur with increasing frequency, nvarsmooth sinusoidal with a further increase of the distance Rvarfrom the axis of rotation of the hub 20 to the point of hinged attachment 26 on the rim 20 of the pull rope 25, which will lead to further smooth sinusoidal speed Vvarthe translational motion of the cable hangers 5, but now up during the stroke (see Fig) until reaching the maximum value (again, see Fig) and one complete cycle.

For clarity in tables 1-3 presents examples of implementation of the proposed method of production in comparison with typical modes of production using conventional pumping units. Set the options (see Fig.6-10 and 14-22): inner diameter of the rim 19 of the DNR=1800 mm; outer diameter step is s 20 d drug=800 mm; frequency of rotation of the hub 20 n=10 rpm Then for different values of the eccentricity e of the proposed method allows to obtain the following characteristics:

Table 1
№ p/pThe eccentricity e, mmThe angle of rotation of the rim, hailVariable radius RvarmmThe frequency of rotation of the rim nvarrpmThe average speed of the rim ncprpmThe frequency of rotation of the rim nvarrpmThe average speed of the rim ncprpm
10500,0010,006,00
245678,89of 13.588,15
390 984,8919,7011,82
41351216,1924,3214,59
54001801300,0026,0018,0015,6010,75
62251216,1924,3214,59
7270984,8919,7011,82
8315678,89of 13.588,15/td>
9360500,0010,006,00

Table 2
№ p/pThe eccentricity e, mmThe angle of rotation of the rim, hailVariable radius RvarmmThe frequency of rotation of the rim nvarrpmThe average speed of the rim ncfrpmThe frequency of rotation of the rim nvarrpmThe average speed of the rim ncprpm
10600,0010,007,00
245719,8412,008,40
390948,6814,3810,07
41351132,6018,8813,22
53001801200,0020,0014,5014,0010,15
62251132,6018,8813,22
7270948,6814,3810,07
8315719,8412,00 8,40
9360600,0010,007,00

Table 3
№ p/pThe eccentricity e, mmThe angle of rotation of the rim, hailVariable radius RvarmmThe frequency of rotation of the rim nvarrpmThe average speed of the rim ncprpmThe frequency of rotation of the rim nvarrpmThe average speed of the rim ncprpm
10700,0010,008,00
245771,6512,86 10,29
390921,9513,1710,54
41351050,9915,0112,01
52001801100,0015,7113,0812,5710,47
62251050,9915,0112,01
7270921,9513,1710,54
8 315771,6512,8610,29
9360700,0010,008,00

As can be seen from Table 1, when the eccentricity e equal to 400 mm, and the minimum rotational speed of the rim is 10 rpm, average speed rim ncpis 18 rpm, that is more than 1.8 times. Setting the minimum frequency of rotation of the rim, is equal to, for example, 6 rpm, the resulting average frequency of rotation of the rim ncp;equal in this case 10,75 rpm, exceeding for this case the minimum specified frequency at 1.8 times. Therefore, improving the performance of oil production will amount to 80%.

From Table 2 it follows that when the eccentricity e equal to 300 mm, the average speed of the rim ncpis 14.5 rpm Setting minimum frequency of rotation of the rim, equal to 10 rpm, and say 7 rpm, the resulting average frequency of rotation of the rim ncpequal 10,15 rpm As can be seen, the average frequency for a complete turnover of the rim exceeds the minimum frequency of 1.45 times.

And finally, when exce is tristate e, equal to 200 mm (see Table 3), the average speed of the rim ncpis 12,86 rpm At the minimum rotational speed of the rim is 8 rpm, average speed rim ncpwill be 10,47 that exceeds the minimum 1.3 times.

Are presented in Tables 1-3 indicators are equally applicable to devices using and drove, and pulling ropes, as the ratio of variable radius Rvarhub 20 and the rim 19 and the rotation speed nvarthe same for both the above options except for more navorot the pull rope on the hub.

The proposed machine-rocking carries the oil extraction method as follows.

According to the calculated average frequency swing ncpequalizer 3, set the average speed rims 19, calculate the value of eccentricity e, corresponding to the amount of displacement of the frame platform 14 relative to the support frame 18. Frame platform 14 choose to unpin it from the support frame 18 including, for example, by a screw pair, the magnitude of the eccentricity e and again securely attach the same set of bolted connections.

Next to the cable suspension 5 fixed surface rod 6 and the entire rod string connected to the sucker rod pump plunger (not shown). From this moment on, soft start motor 13 through V-belt transmission 12 to confuse the cabins in the work of the gearbox 11. When the output shaft of the gearbox 11 must rotate clockwise when the offset eccentricity to the right (see Fig.6) and counterclockwise at offset eccentricity to the left (see figure 1) on the part of the observer.

Through hub 20 mounted on the ends of the output shaft of the reduction gear 11, the torque is transmitted measured including carriers 21 and the rollers 23, is placed through the slots 22 and pivotally fixed on a single fingers. In turn, single fingers pressed into the ends of the rims 19, transmits the rotation of the rim 19. During rotation of the rims 19, rigidly connected with the respective cranks 10, with the help of connecting rod 8 through the yoke 7, the force is transferred to the rocker 3, forcing him to make a swinging movement. The head 4 of the balancer 5 specifies the reciprocating movement of the cable suspension 5 and, through the mouth of the shaft 6, further plunger sucker rod pump.

The difference between the proposed group of inventions is that swinging movement of the rocker 5 accelerated in the upper position of the head 4 of the rocker 5 and slowed down at the lowest point of its location. Respectively, and the cable suspension 5 synchronously reproduces the reciprocating movement then increasing to a maximum

the values of Vvar maxthen falling to the minimum value of Vvar minsinusoidal.

It should be noted that substantially the growth performance usgn in General, due to the increased frequency of the swing, you must pay special attention to the fill factor of the pump for which, if necessary, it is necessary to apply suction and discharge valves, pumps, sucker rod pump with increased wall sections to achieve the effective filling of extraction pumps.

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

- significantly increase (up to two times or more) the performance of the oil production with the use of SRPS, further bringing this type of pump for this indicator for high-performance electric submersible pumps (ESPs);

- significantly speed up the idle speed and slowing down in a sinusoidal law as it approaches the lower critical point, which further favors the increase of the filling ratio of a plunger pump under the pressure of the column of well fluid above the submerged into the well pump sucker rod pump, as some slowdown at the finish idling gives you additional time to fill the internal cavity of the pump above the plunger;

- to reduce the negative impact of dynamic processes at the beginning of the stroke up at the expense of some computational speed reduction reciprocating motion at the lowest point compensation, and a gradual increase in speed at the highest point on the sine law;

to reduce leakage in the gap plunger pairs with acceleration of the stroke when the steady-state dynamic mode, as reduced by the time of the possibility of such leaks in the same length of stroke of the plunger.

1. The oil extraction method using a sucker rod pump comprising changing the frequency of rotation of the crank pumping unit and agreed with him by changing the angular velocity of the swing of the balance wheel change speed of the reciprocating movement of the wellhead rod, characterized in that the rotational speed of the crank, and agreed with her speed reciprocating motion of the rod change in a sinusoidal manner, smoothly accelerating stroke, whereby forward movement of the rod to the upper reaches its maximum speed when the vertical position of the connecting rod and crank at the bottom, and proportional slowing idling, whereby forward movement of the rod down reaches the minimum speed in vertical position connecting rod and crank at the upper point, and the speed of the stock at the beginning of the stroke and at the end of idling reduced by the amount, less the average speed of the reciprocating motion of the rod.

2. A conventional pumping unit for oil extraction using sucker rod pump, containing a support frame, a rack on which the use of the hinge is mounted rocker having on one side the head with rope suspension and estuarine stock, and on the other hand is pivotally suspended from the yoke with spaced on both sides of the rack rods, each the second of which is connected to the crank, which is attached a counterweight, as well as containing the gearbox input shaft by V-belt transmission is connected with an induction motor, characterized in that the cranks mounted on rims that are installed with the possibility of circular motion in the frame of roller bearings or roller bearings placed at the perimeters of the Windows, made in the vertical frames, which are fixed on opposite sides of the base frame, and a gear and a motor mounted on the frame platform installed, in turn, on a support frame can move along the direction of the balancer, and at the ends of the output shaft of the gearbox in the plane of circular motion rims mounted hub, the outer diameter is made smaller inner radius rims, the hubs are attached to the carrier, each of which has a through radial or oblique groove within which is placed a roller mounted hinge with bearing on the finger is pressed into the end of the corresponding rim ahead in the direction of rotation at an angle of 90°and less than or more than this value, relative to the point of attachment to the rim of the crank.

3. The machine rocking chair according to claim 2, characterized in that the through radial grooves have drove at the ends remote from the axis of rotation of the hub, smooth bends about the Yves direction of rotation.

4. A conventional pumping unit according to claim 2, characterized in that the through inclined slots drove performed with a deviation in the direction of rotation of the end of the groove remote from the axis of rotation of the hub.

5. A conventional pumping unit according to one of claim 2 to 4, characterized in that the through slots of the carrier is made curved or in the form of an arc of a circle, or other smooth geometric dependencies.

6. A conventional pumping unit according to one of claim 2 to 4, characterized in that the through slots of the carrier is made in the form of a combination of rectilinear and curvilinear sections.

7. A conventional pumping unit according to claim 3 or 4, characterized in that inside the through groove of each of the led instead of the movie posted a slide mounted through the hinge (e.g. bearing) on the finger is pressed into the end of the corresponding rim.

8. A conventional pumping unit for oil extraction using sucker rod pump, containing a support frame, a rack on which the use of the hinge is mounted rocker having on one side the head with rope suspension and estuarine stock, and on the other hand is pivotally suspended from the yoke with spaced on both sides of the beam connecting rods connected to the crank, which is attached to the counterweight, as well as containing the gearbox input shaft by V-belt transmission connected to the motor, characterized in that the cranks for repleni on rims, installed with the possibility of circular motion in the frame rollers or roller bearings placed at the perimeters of the Windows, made in the vertical frames, which are rigidly attached to opposite sides of the base frame, and the gearbox and the motor is rigidly mounted on the frame platform mounted in turn on a support frame can move along the direction of the balancer, and at the ends of the output shaft of the gearbox in the plane of circular motion rims mounted hub, the outer diameter is made smaller inner radius of the rim, wherein the outer diameter of each of the hubs made circular groove, in which is laid a pull rope, one end pivotally attached to the hub, and the other end connected with the corresponding rim also hinge set ahead in the direction of rotation at an angle of 90°and less than or more than this value, relative to the point of attachment to the rim of the crank, in addition, pulling the ropes, arranged in the annular groove of the hub, must be pre-screw on the hub by an amount providing a uniform transfer of load along the arc of coverage of the outer diameters of the hubs in the tensioning process, but not exceeding the total perimeter of the outer circumference of the hub, in order to exclude the winding of each rope with the constituent itself during each full rotation about its own axis of rotation, moreover, the radius of the grooves grooves on the hub cross-section must correspond to the radius of the pull rope with the necessary clearance for easy installation and a snug fit to the groove that provides a smooth distribution of the load over the arc of contact.



 

Same patents:

FIELD: oil industry.

SUBSTANCE: invention refers to oil industry and namely to methods of simultaneous separate operation of two beds of one and the same well. The method involves lowering and installation of a packer in the well between beds, production tubing, upper and lower pumps connected in series and arranged in the production tubing and connected with rods to a common top's drive. Pump inlets are connected to the spaces above the packer and below the packer correspondingly. The upper pump outlet is connected to the flow column, and the lower pump outlet - to the upper pump inlet. Then the drive is brought into operation and adjusted so that proportional pump capacity of the translational movement speed of rods with plungers can be changed. Pumps being installed are screw-type; production tubing before being lowered is equipped with couplings with calibrated central channels arranged below the pump shells fixed on the production tubing. Upper coupling is arranged within the channel connected to the space above the packer. Pump screws are equipped with upper and lower plungers, the upper one of which is through-type for longitudinal liquid flow. Diametres of plungers and screws are decreased downwards in order to pass through the shells and couplings which are not appropriate to them when being lowered. The stock is geared with the top's drive as well. Translational movement is performed in pulse mode; upwards from medium operating position for lower piston to interact with lower seat and for lower screw to come out of the shell upwards thus cutting off the space below the packer and performing the production only from upper bed, and downwards - for upper piston to interact with upper seat thus cutting off communication channels and the space above the packer and for upper screw to come out of the shell downwards and performing the production from lower bed.

EFFECT: method allows separate investigation of properties of beds and their production by consequent cutting off beds and the pumps corresponding to them, allows working with well production containing a great number of mechanical particles because only screw pumps are used for lifting the well production, as well as continuing production without replacing a differential pump and at changing the bed productivity ratio in the course of time.

2 dwg, 2 cl

FIELD: engines and pumps.

SUBSTANCE: invention relates to oil production. Proposed drive comprises drive link shaft, drum fitted on support, circular housing consisting of base and cover with branch pipe communicating with pump-compressor pipe. Driving link shaft extension has coaxial gear with cylindrical ledge on free end face. Ledge diametre equals that of gear pitch line. There is lengthwise slot on the end face cylindrical surface. Gear wheel seats parallel to driving link shaft. Toothed concave and convex rims are arranged inside the housing. Coaxial barrels are arranged on faces of aforesaid rims. Two or more brackets are rigidly attached to the flat surface of base, the said brackets featuring arc-like concave stop. One end of concave stop is arranged above free end of cylindrical stop. Similar brackets support another arc-like convex stop. One end of convex stop is arranged above free end face of driving link shaft cylindrical ledge. Arc-like stop is arranged coaxially with latter and on brackets. There is a plate with longitudinal slot arranged between arc-like stops and housing cover, and rigidly attached to adjacent cheek of the drum. Slot outer surface width is smaller than slot bottom width. Additional flexible element is wound up on the drum. Additional hole with vertical branch pipe is arranged on the housing cover, in symmetry with the hole with flexible element. The said vertical branch pipe is tightly jointed to vertical cylinder with counterweight. The latter is jointed to second end of additional flexible element. There are some other versions of drive design.

EFFECT: higher drive efficiency.

11 cl, 16 dwg

FIELD: engines and pumps.

SUBSTANCE: invention is related to oil production industry and may be used for operation of production wells, including the ones with highly viscous produce, and also in wells of small diametre. Bottomhole pump set includes sucker-rod pump comprising cylinder, receiving valve, plunger with controlled injection valve, which is connected to string of pump rods with positioners, packer and relief device. Downstream relief device hollow tailpiece is arranged, which consists of upper and lower parts. Additional relief device is located in tailpiece. Packer is arranged in the form of self-sealing collars with distance between neighboring self-sealing collars that exceeds distance between ends of pipes in coupler joints of flow string, and support. Downstream packer and upstream support tailpiece is equipped with side holes. Additional relief device is arranged in the form of cylinder connected to lower part of tailpiece, with side channels that communicate to internal cavity of tailpiece and hollow piston connected to upper part of tailpiece, with the possibility of limited axial displacement downwards relative to cylinder with tight overlapping of connection between side channels of cylinder and internal cavity of tailpiece.

EFFECT: provides for considerable reduction of laboriousness of installation -dismantling and makes it possible to reduce time required for set lowering-lifting in well, and also to expand field of its application due to possibility to use it in wells of small diametre.

2 dwg

FIELD: mining.

SUBSTANCE: installation consists of the first and the second cylinders. The first cylinder is equipped with a side valve with a filter and from below it is connected with a packer, which in its turn is connected with the second cylinder equipped with a side valve with a filter and a side opening. The second cylinder is connected to an adaptor equipped with a valve with a filter and connected to a polished tail, which is pressure tight installed in a polished cylinder of the packer-cut-off plate. Inside the first and the second cylinders there are installed plungers with valves, rigidly connected between them with a rod equipped with channels for produced liquid flow. The plungers are connected with a column of rods. The first cylinder is connected with a flow string.

EFFECT: there is facilitated working capacity at any values of pressure of operated reservoirs, also efficiency of pump in accordance with reservoir yields and possibility to operation of only one reservoir at complete isolation of another.

1 dwg

FIELD: mechanics, oil and gas industry.

SUBSTANCE: unit is intended for using as deep well pump for oil production from oil wells. The unit consists of a platform, pedestal with gearbox and rack being installed on it, electric motor coupled with gearbox through multiple V-belt drive. Differential crank converting mechanism is installed on the gearbox output shaft. The above mentioned converting mechanism contains two cranks interrelated through planetary gear. The central crank is rigidly installed on the gearbox output shaft. Driving crank with tension pulley is mounted on the central crank output shaft. Polished rod carrier bar is installed at the other side of gear box. The rack is installed on pedestal between polished rod carrier bar and tension pulley of driving crank. The oscillating equal-arm rocker is movably mounted on the rack and immovable heads are rigidly fixed to the rocker ends. From the side of converting mechanism cranks, the rocker head is connected with tension pulley of driving crank, while the other rocker head is coupled with polished rod carrier bar from the side of the above bar. The rack and rocker are implemented so that the rocker can rotate around its axis. The rocker head edges are in vertical plane, which is at some distance away from the wellhead. It is provided by the invention that balanced pumping unit design is implemented so as rack with rocker and converting crank mechanism being placed at one side of gearbox. Comfortable conditions for drive repair operations.

EFFECT: linear reciprocal motion of tension pulley is ensured on driving crank.

3 dwg, 4 cl

FIELD: engines and pumps.

SUBSTANCE: invention relates to oil production, namely to pumping units to force extracted local water into petroliferous stratum to keep up formation pressure therein. The proposed unit comprises a casing string coupled with a deep-well pump incorporating a cylinder with suction valve and a plunger with pressure valve lowered into operating well string with perforated parts opposite the petroliferous stratum and water producing formation. The wall packer is fitted on the pumping pipe string end and closes the hole clearance above the water producing formation. The tubular pump is arranged in the pumping pipe string above its end. The cylinder is furnished with lateral holes arranged at such a level that, with the plunger in its BDC, the said holes are open and communicate hydraulically the pumping pipe string inner space with the wall hole clearance above the packer, and, with the plunger in TDC, the said holes are blocked.

EFFECT: possibility to use whatever-type pump, to adjust forcing water a integral system of keeping up formation pressure and to exploit petroliferous stratum free areas with weakly-permeable reservoirs thanks to independent pumping in.

1 dwg

FIELD: engines and pumps.

SUBSTANCE: invention is related to oil industry and may find application in oil production from two beds of single well. The plant includes sucker-rod pump with plunger, cylinder, suction and pressure valves. Cylinder is equipped with side valve with filter. Auxiliary cylinder with side holes is fixed in cylinder, as well as jacket with provision of annular space between auxiliary cylinder and annular space jacket. Lower end of cylinder is plugged with plug. Suction valve, filter and tail with packer at the end are fixed on jacket. Plunger is arranged as combined, consisting of upper and lower plungers connected with stem with valves, with installation of upper plunger inside cylinder and lower plunger inside auxiliary cylinder. Lower plunger and stem have channel for communication of space above and under lower plunger. Upper plunger and stem have channel for space connection under upper plunger with inlet to upper plunger valve.

EFFECT: provision of serviceability at any values of pressure in operated beds and possibility to operate only one of beds.

3 dwg

Well pump drive // 2353807

FIELD: engines and pumps.

SUBSTANCE: device is designed for application in the field of oil production by well pumps. Drive comprises guide link shaft having gear and drum joined to electric motor, annular body installed on support and having base and cover with nozzle joined to pump-compressor pipe. Cylindrical protrusion is arranged on free end of guide link shaft gear. Long slot is arranged on cylindrical surface of cylindrical protrusion at the end. Gear wheel is installed parallel to gear and at the same distance from base axis. It is arranged with dimensions and cylindrical protrusion similar to dimensions and cylindrical protrusion of gear. Concave gear ring is installed inside body, and convex gear ring is installed on cover. Teeth of convex and concave gear rings are engaged with gear and gear wheel teeth. Coaxial cartridges are arranged on ends of convex and concave gear rings. At least two brackets are rigidly fixed and installed on internal flat surface of base perpendicular to this surface. Arc-shaped concave thrust is fixed at free ends of brackets, at that it is arranged with internal diametre equal to external diametre of convex gear ring cartridge external diametre, and internal diametre equal to sum of external diametre of this cartridge plus double depth of long slot. Another arc-shaped convex thrust is installed and fixed to free ends of brackets, and it has external diametre equal to internal diametre of concave gear ring cartridge. There is plank installed between arc-shaped thrusts and body cover, and it has long slot in the form of, for instance, dovetail. Drive is equipped with detector of concave and convex gear ring rotations number. Arc-shaped thrusts of gear and gear ring cylindrical protrusions are separated into two parts. Hinge axis is installed perpendicular to internal end surface of base and is installed in hole arranged in separated end of arc-shaped thrust with inclined surface. Arc-shaped thrusts with inclined surfaces are equipped with fixed joined spring-loaded levers. Free end of every lever contacts with side cylindrical surface and bottom of sprocket hub groove. Base has additional nozzle connected to counterbalance cylinder and equipped with flexible element. Flexible element is fixed by its one end to drum, and by the other - to counterbalance. Additional nozzle is connected to pump-compressor pipe of another well. In order to define place of gear ring installation, with combined apertures of long slots of cylindrical protrusion of gear and cartridge of concave gear ring, gear is turned by 180 degrees to combine apertures of slots of cylindrical protrusion of gear and cartridge of convex gear ring, gear ring convex cartridge is turned to the side of gear wheel axis installation to match line passing along axis of symmetry of cross section of long slot of convex gear ring cartridge, with middle of arc passing along circumference of concave gear ring reference diametre, selected from axis of symmetry of cross section of nearby long slot of concave gear ring cartridge to the side of gear ring installation place, and equal to length of gear reference diametre circumference, afterwards line matched with arc middle is projected to surface of base, and mark is made in the middle between circumferences of reference diametres of concave and convex gear rings on this line.

EFFECT: increased service life of well pump due to provision of electric motor rotation without stops.

6 cl, 17 dwg

Well rod pump drive // 2351802

FIELD: engines and pumps.

SUBSTANCE: invention relates to oil and gas production and is operated for oil extraction by well rod pumps in simultaneous operation of two formations using two plunger pumps. The proposed drive represents a pumping unit additionally incorporating props arranged on the frame to accommodate rigidly interconnected pulleys whereto one ends of cables are fastened to form, two by two, cable pairs. One pair is connected by its one end with the pumping unit suspension, the other pair is connected to the second drill rod string and the third one is coupled with the balance box arranged between the aforesaid props to be moved there between driven by rollers. To vary the drill rod string length travel, the pulley diameters are selected subject to the drill rod string length-to-length ratio.

EFFECT: higher efficiency of oil extraction, lower power consumption.

1 cl, 2 dwg

FIELD: oil and gas industry.

SUBSTANCE: invention refers to oil and gas industry, particularly to pump installations of well. The installation consists of production string, of a column of hollow rods, of a packer and a differential pump with upper and lower hollow plungers. The suction valve of the upper section of the differential pump is installed at side, while the pressurising one - in a bypass channel of the upper section conjugated with the cavity of the production string. The bypass channel is made in the upper plunger. The upper plunger is assembled on the hollow rod so, that fluid can overflow; the upper plunger is designed to perform limited axial travels. From below the bypass channel is equipped with a seat of the pressurising valve, while the hollow rod is equipped with its locking body arranged on the exterior surface of the hollow rod and with a pusher interacting with plunger from above.

EFFECT: simplification of installation design, increasing of its efficiency, particularly at high viscosity of reservoirs, facilitation of installation regulating for reservoir yields.

2 dwg

Well pumping unit // 2244852

FIELD: lifting of liquids from deep wells.

SUBSTANCE: proposed unit contains submersible pump, pressure tubing string, drive shaft consisting of sucker rods whose ends are provided with slots and which are installed inside connectors. The latter are made in form of bushing with inner cylindrical ring groove in middle part and through longitudinal slots on end sections in number corresponding to number of slots on sucker rods, and blind slots located between through slots. Blind slots are made open from side pointed to cylindrical ring groove and are through in radial direction.

EFFECT: improved operation reliability, reduced service expenses, simplified design.

5 dwg

Lock support // 2247261

FIELD: oil producing industry.

SUBSTANCE: invention relates to lock supports of insert sucker-rod pumps. Lock support housing accommodating spring-loaded valve with retainer. Spring of valve is installed on stop. Support has two cylinders of different diameters, upper cylinder being connect by sub to insert pump. Spring-loaded valve is provided with guides. Hole from side of retainer in form of sheared dowel is made in one of guides, and ports are made in other guide and in lower cylinder of smaller diameter.

EFFECT: simplified design, improved reliability.

1 dwg

FIELD: oil production industry.

SUBSTANCE: proposed plant is designed for completion of oil and gas wells producing hydrocarbon materials. Plant contains deep well pump with delivery and suction valves and pump drive made in form of stepped cylinder with piston. Pressure accumulator is made in form of elastic ball placed in larger step of cylinder. Pump plunger is sealed in upper part by gland packing. Interaction of pump piston with drive is provided by water hammer. Oil is used as intermediate liquid in drive.

EFFECT: provision of effective recovery of oil or gas at minimum expenses.

1 dwg

FIELD: oil industry.

SUBSTANCE: method is based on measurement of actual current of engine at double drive of rod with working plant, comparison of its values at upward rod drive and downward rod drive, stopping plant, moving loads on crank with repeated launch, measurement and comparison of said current values. Additionally, during operation of device, time of downward and upward rod drives is measured. On basis of measured current values its average quadratic values are determined during upward and downward rod movement on basis of given formulae. Then value of balance coefficient Kbal is determined. When Kbal=1 plant is considered balanced. In other case plant is stopped and loads are displaced relatively to current position proportionally to value of Kbal.

EFFECT: higher efficiency and effectiveness.

1 dwg

FIELD: general engineering; oil producing industry.

SUBSTANCE: proposed surface drive of submersible screw pump contains reduction gear with vertical input and output shafts, engine arranged on side surface of reduction gear housing and installed for displacement, torque transmission V-belt drive and brake device. Brake includes two spaces sealed relative to each other. One space filled with oil accommodates shaft of reduction gear with overrunning clutch fitted on. Second space non-filled with oil, accommodates friction device consisting of friction member and disk which serves simultaneously as body of overrunning clutch. Adjusting device acting onto friction member is provided to regulated brake torque.

EFFECT: improved reliability and efficiency of drive in operation, provision of stepless killing of reactive torque of rotating string with engine shut down, prevention of turning out of threaded joints.

4 cl, 5 dwg

FIELD: positive-displacement machines or pumps.

SUBSTANCE: clamping device is mounted at the well mouth and comprises housing with the recess for mounting and dismounting hinged jaw provided with socket for setting the collar of the pump rod. The jaw is pivotally connected with the housing. The setting socket for the head of the rod is made between the housing and jaw. The section of the contact surface is made on the housing, and the axis of the pivot can move a distance from the contact surface of the socket in the housing.

EFFECT: enhanced reliability.

2 dwg

Pumping unit // 2260713

FIELD: oil producing industry.

SUBSTANCE: device is designed for mechanized recovery of oil and gas by well sucker-rod pumping units. Proposed pumping unit has base, Sampson post, double-arm rotary walking beam with flexible suspension of rod, crossmember with connecting rods, cranks with counterweights. Front counterweight in direction of movement has longitudinal slot with guides and disk-weight installed for movement square to axis of crank rotation. Mass of front counterweight with disk-weight is equal to mass of rear counterweight in direction of movement. Disk-weight can be fixed by means of stop pin for balancing the pumping unit. Stop pin is installed in holes of housing of front counterweight and disk-weight. Thanks to it torque on cranks at lifting of sucker-rod string is increased and dynamic loads on electric motor drive are equalized.

EFFECT: reduced power consumption, increased economy.

2 cl, 3 dwg

FIELD: oil producing industry.

SUBSTANCE: device is designed for driving deep-well sucker-rod pumps. In proposed differential pumping unit differential crank mechanism is used as transforming mechanism providing straight-line reciprocation of point of attachment of tension pulley on drive crank. Said transforming mechanism is installed on output shaft of reduction gear from one side. Post with guide pulley is arranged at this side also. Axle of part is in vertical plane passing through axis of reduction gear output shaft. Radii of central and drive cranks are equal to each other. Tension pulley is mounted of drive crank over which flexible member is passed. Said tension pulley is coupled through guide pulley installed on post with polished rod carrier bar. Cranks are interconnected and they rotate in different directions. Length of stroke is equal to sum of four radii of cranks. Pumping units are most efficiency at length of stroke from 2.5 to 5 m.

EFFECT: provision of larger length of stroke at more rational design.

3 cl, 3 dwg

FIELD: mechanical engineering; well pump drives.

SUBSTANCE: invention is designed for use in units operating well pumps designed for lifting liquids from depth. Proposed device contains base on which frame with platform is installed for drive unit with hole to drive output link. Platform is connected with frame by hinge joint for turning relative to axis in plane parallel to axis of hole in platform.

EFFECT: improved convenience in operation owing to provision of access to well, wellhead equipment and drive at repairing and servicing of wellhead equipment and drive without demounting of drive.

7 cl, 1 dwg

FIELD: oil production, particularly oil and gas well development for hydrocarbon material.

SUBSTANCE: device comprises check valve, piston, receiving windows, depression chamber and valve with spring. The device is made as swabbing means and depression chamber connected one to another by threaded subs. The swabbing means consists of rope fastening unit, cylinder, hollow shaft, piston and valve with spring. Cylindrical valve is installed in lower part of depression chamber. The cylindrical valve is made as a sleeve with beveled lower end surface.

EFFECT: increased efficiency of well development due to impulsive action application to productive bed.

1 dwg

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