RU2574651C1 - Downhole equipment for polyfrequency wave treatment of bottom-hole zone of productive formation and flowrate oscillations generator for that - Google Patents

Abstract

FIELD: oil and gas industry.

SUBSTANCE: downhole equipment for the polyfrequency wave treatment of the bottom-hole zone of the productive formation includes a jet pump with a nozzle chamber, a valve-relay, a flowrate oscillations generator under the packer on the pipe string at the depth of the perforation interval, hydromechanical radiator of elastic vibrations, installed in the formation interval above the input channels of the generator. The jet pump has a hydraulic accumulator. The valve-relay has a hydraulic check valve, and is installed under the jet pump, and the generator is made in the form of the hydrodynamic generator of relaxation flowrate self-oscillations.

EFFECT: increased radius of the formation treatment, increased degree and quality of the formation cleaning and intensification of the oil/gas inflow.

19 cl, 7 dwg

Description

The group of inventions relates to the oil and gas industry, as well as to the technique of generating elastic vibrations. The devices can be used as downhole equipment for cleaning the bottom-hole zone of oil and gas-containing strata from clogging materials during development, resuscitation and increasing productivity of wells, for multi-frequency wave action on formations to increase oil recovery, as well as for treatment of water wells, in the mining industry to initiate and intensification of borehole hydraulic mining of minerals, in particular for underground leaching, hydraulic mining of bulk ores. To achieve the highest efficiency of processing the bottom-hole formation zone (PZP), it is advisable to combine the operation of the equipment with the injection of chemicals. The proposed hydrodynamic generators of relaxation flow self-oscillations can also be used for the preparation of finely dispersed emulsions or foam systems of increased resistance, for example, in the chemical and food industries, in flotation mining processes, oil-water emulsions for killing wells, in various technological processes that require intense fluctuations in flow and pressure liquids in acoustic-oceanological studies due to the low frequency of oscillations.

To assess the novelty and technical level of the claimed solution, we consider a number of information known to the applicant from information that has become publicly available prior to the priority date of the invention, technical equipment of a similar purpose, characterized by a combination of features similar to the claimed invention.

A device is known for oil production, development of productive horizons and cleaning of the bottomhole zone (RF patent 2084705, class F04F 5/00, published in BI No. 20, 1997), consisting of a jet pump placed with a packer on a pipe string , a branch filter coupling, a hydrodynamic emitter installed under the packer on a pipe string, which is hydraulically connected to the pressure line through a differential pressure valve.

The disadvantages of the known invention are the low efficiency of processing poorly producing wells that open low-permeability, highly contaminated in the near-wellbore zone, reservoirs, weakening efficiency for deep wells, associated with the need to use powerful pumping units, significant difficulties in combining the operation of equipment with reagent treatment processes due to technical limitations allowable pressure on the production casing.

Also known is a hydrodynamic oscillation generator (RF patent 2087756, publ. BI No. 23, 08/20/1997), comprising a housing, a flow chamber located therein with swirl channels and a main nozzle, a central body installed in the flow chamber with a gap relative to its lateral walls, a pressure line connected to the swirl channels, and an additional line connected to the pressure line through a flow limiter and communicated with the main nozzle through the gap between the central body and the wall of the flow chamber.

A disadvantage of the known generator is the low efficiency of its operation, associated with large losses on the viscous friction of the working fluid in the flow channels and its limited flow rate with acceptable dimensions of the device.

There is also known a method of generating oscillations of a fluid flow and a hydrodynamic oscillator according to the patent of the Russian Federation 2296894, class F15B 21/12, B06B 1/18, according to the application 2005104558/06, 02.21.2005, publ. 04/10/2007. According to this invention, the liquid under pressure is swirled, at least two oppositely directed vortices are created, formed by swirling fluid flows with the same supply pressure, while swirling fluid flows are separated by an intermediate nozzle of a centrifugal nozzle and one of them is connected to a cavity with adjustable elasticity and the other with the outlet nozzle. The hydrodynamic oscillation generator comprises a body with a swirl chamber, swirl channels, an outlet nozzle, a pressure line connected to swirl channels, and a central body installed in the swirl chamber with a gap relative to the side wall, a cavity with adjustable elasticity. The gap is connected to an intermediate nozzle of a centrifugal nozzle having twist channels of opposite orientation to the channels of the output nozzle and communicated with a cavity with adjustable elasticity.

According to the author, "due to the introduction of the intermediate nozzle of the centrifugal nozzle in a cavity with adjustable elasticity, the pressure created by the liquid vortex in the vortex chamber increases, which is additionally pressed through the intermediate nozzle of the centrifugal nozzle by the liquid vortex of the swirl chamber." From this statement of the author it follows that by increasing the number of swirling fluid flows separated by intermediate nozzles, it is supposedly possible to additionally increase the pressure in the cavity with adjustable elasticity, and in the limit to create even higher pressure in the pressure line, but this contradicts the laws of physics. Moreover, the fluid enters the swirl channels under the same pressure. Pressure is an additive, not a vector quantity. Therefore, the resulting pressure in the cavity with adjustable elasticity cannot be determined by the sum of the centrifugal pressures of both vortices, but depends only on the centrifugal pressure developed by the liquid vortex of the swirl chamber with the outlet nozzle, even though the hydrostatic pressure is always less at the outlet of the nozzle in the medium being processed. The execution of the intermediate nozzle greatly affects the operation of the generator. The centrifugal pressure created in the intermediate twisting chamber prevents the flow of fluid from the cavity with adjustable elasticity and leads to the creation of residual pressure in it and the irrational use of the elastic properties of the cavity. In addition, due to the presence of a nozzle, the intermediate chamber has a narrowing in the vortex chamber, which accordingly increases the path and prevents the flow of fluid from the chamber and cavity with adjustable elasticity towards the outlet nozzle. All this reduces the speed and intensity of rotation of this flow and, as a result, the interaction decreases when mixed with a liquid vortex of the opposite twist, the speed of outflow from the output nozzle decreases, and compared to even the RF patent adopted by us for the prototype No. 2144440, the oscillation amplitude is significantly reduced fluid flow.

Closest to the proposed invention is a downhole equipment for processing the bottom-hole formation zone (RF patent No. 2175718, class No. 21B 43/25, published in BI No. 31, 2001), containing a jet pump with a housing mounted on a packer on a pipe string including a mixing chamber, a nozzle chamber with a passage through a packer and a filter sleeve, inside which a relay valve and a flow or pressure regulator are installed. A hydrodynamic emitter is installed under the packer on the pipe string at the level of the perforation interval. The relay valve is equipped with a time relay and is installed between the pressure regulator and the emitter. In parallel with the relay valve, a transfer channel is made. The hydrodynamic emitter is made in the form of a self-oscillating low-frequency generator of flow fluctuations.

The disadvantages of the device are due to the fact that the energy of the pumping unit is unproductive; during the cycle of increasing bottomhole pressure it is difficult to ensure the generation of high-amplitude pressure fluctuations, and this is an important condition for processing efficiency, especially with a large radius of the sealed zone near the wellbore. In addition, the known device does not allow to fully implement, together with the action of elastic vibrations, a reagent effect on the formation, without which it is difficult for certain categories of wells to obtain an acceptable result. Due to the presence of a time relay in the relay valve, the operation of the pump will change dramatically - when the relay closes, the liquid flow will sharply decrease due to the operation of only the jet pump and accordingly the pressure will increase up to a dangerous value, which requires constant attention and switching the operating mode of the pump unit.

A known method of exciting oscillations of a fluid flow and a hydrodynamic oscillator according to the patent of the Russian Federation No. 2144440, class. B06B 1/20, which is the closest to our technical solution. According to this invention, the liquid is twisted under pressure, at least two oppositely directed vortices are created, formed by swirling fluid flows with the same supply pressure, the periphery of which is hydraulically connected with a cavity with adjustable elasticity. The hydrodynamic generator comprises a housing, a vortex chamber installed therein with swirl channels and an outlet nozzle, and a pressure line connected to swirl channels. A central body is installed in the vortex chamber with a gap relative to its side wall. The generator is equipped with a cavity with adjustable elasticity, communicated through passage openings with the vortex chamber and through the aforementioned gap with the outlet nozzle, and the swirl channels are made in at least two cross-sectional planes of the swirl chamber with a mutually opposite swirl orientation and are connected to the pressure manifold.

The disadvantages of the known device are the relatively low efficiency of converting hydraulic energy into vibrational due to the overhead of hydrodynamic energy. The design features of the device make it difficult to optimize the generation of oscillations for working with changing overpressure in the pressure line or at the exit of the nozzle. This is due to the fact that the operation of the generator is quite sensitive to the size of the twisting channels, the distance between their cross-sectional planes of the vortex chamber and to the width of the gap between the central body and the side wall. Therefore, when they are eroded due to abrasive and other wear, the generator’s work will deteriorate sharply, and for certain flow ratios through the swirl channels in the oppositely directed vortices, the oscillation amplitude either turns out to be low or the self-oscillation mode can be disrupted. In addition, since the fluid is supplied under the same overpressure, and therefore, by a source of injection, for example, a centrifugal pump, a predetermined pressure value is maintained in the pressure line, then when the static pressure in the medium is increased, the generator may become unstable, up to the failure of self-oscillations, since In this case, the total pressure drop across the generator will decrease and, accordingly, the flow rate will decrease, which limits the scope of its application only for conditions with a free exit, without much resistance to leak fluid from the nozzle, such as in open containers.

The objective of the invention is to increase the efficiency of downhole equipment while increasing reliability, expanding the functionality and operational properties, in accordance with the needs of the tasks and technical capabilities of injection pumps, the rational use of energy from the pump unit, as well as increasing the efficiency of the hydrodynamic generator, increasing the amplitude of flow fluctuations with acceptable dimensions and parameters for the supply of working fluid, for example, vanishing and injection pressure.

The problem is solved in that the known downhole equipment containing a jet pump with a nozzle chamber, a valve relay, a flow oscillator under the packer on the pipe string at the level of the perforation interval, according to the invention, is equipped with a hydromechanical elastic oscillator installed in the formation interval above the input channels generator, the jet pump is equipped with a hydraulic accumulator, the relay valve is equipped with a non-return valve and is installed below the jet pump, and the generator is made in the form of a hydrodynamic generators of the relaxation rate of oscillation.

In this case, the hydromechanical emitter of elastic vibrations is made in the form of a converter of fluctuations in the pressure of the working fluid into mechanical vibrations of movable rigid elements for transmitting vibrations through a perforated production string into the formation. As an embodiment of the most rational and reliable design, the hydromechanical emitter includes a housing with an axial channel hydraulically connected to at least three cylinders radially located in the housing with hermetically mounted pistons, the outer side of which is in the form of concentrators with a contact area larger than the area of perforations at the same time, from the side of the axial channel and outside the housing, the piston movement limiters are made, and the pistons themselves are equipped with return springs.

It is advisable to perform the relay valve in the form of a housing with radial drain channels and spring-loaded ball clamps, as well as with a cylindrical cavity located along the housing axis with a seat installed in its lower part, spring-loaded shut-off-control element and non-return hydraulic valve, which respectively communicate with the supply and direct-flow channels, the locking-regulating element contains a conical and cylindrical part with the possibility of its movement inside the cylindrical cavity, and on the cylindrical part the locking and regulating element is made around the circumference of at least two grooves with conical sides, while in the initial position of the locking and regulating element, the retainer balls are located in the groove far from the saddle.

The hydraulic accumulator is rationally performed in the form of a terminated elastic hose with gas located in a perforated casing.

To improve consumer properties, it is rational to carry out a jet pump in the embodiment where the nozzle chamber is equipped with a check valve, the lower cylindrical part of which has sealing rings and is installed in the cylindrical cavity of the compensator with the possibility of telescopic movement, while the cylindrical cavity is communicated by channels with the external surface of the compensator and the annulus and before entering the channels a filter is installed.

At the outlet of the jet pump, a flow swirl may be installed.

Downhole equipment can be additionally equipped with a hydro-pulse source of oscillations hydraulically connected to a hydrodynamic generator of relaxation self-oscillations of the flow rate.

A hydrodynamic generator of relaxation flow self-oscillations can be installed in the saddle.

Downhole equipment can be additionally equipped with a mechanical source of elastic vibrations, which is connected with a hydrodynamic generator of relaxation flow self-oscillations and is made in the form of a transducer of axial mechanical movements of the generator into mechanical impacts on the column.

Improving the efficiency of the proposed downhole equipment is achieved by the fact that at the stage of the wave action during the operation of the hydrodynamic generator of relaxing flow oscillations (hereinafter the generator) simultaneously with the transmission of regular vibrations from it to the formation through perforations, additionally mechanical vibrations are emitted directly through the production casing into the formation using hydromechanical emitter of elastic vibrations. In addition, at the stage of depressive effect during the operation of a jet pump equipped with a hydraulic accumulator, due to the presence of a check valve-relay with a non-return valve, low pressure pulses (implosions) and backward shock waves reflected from the jet pump, which are transformed into elastic ones, are created in the sub-packer space and the reservoir interval fluctuations in the formation itself. Equipping the downhole equipment with a hydro-pulse oscillation source or a mechanical emitter allows additionally to excite elastic vibrations. The excitation of oscillations by devices is closely related to the operation of the jet pump. In addition, the operation of a hydromechanical emitter, hydroimpulse source, or mechanical emitter is inextricably linked with the operation of the generator, with each of these devices affecting the PZP at different frequencies, which, when operating simultaneously, ensures the poly-frequency of wave processing. This increases the efficiency of processing the bottom-hole formation zone. In total, the efficiency of downhole equipment increases, the functional capabilities and operational properties expand in accordance with the needs of the problems being solved and the technical capabilities of injection pumps, and both the generator and the jet pump operate in optimal mode during well treatments with little or no reservoir fluid inflow, associated with the maturation of PZP.

The task is also achieved by the fact that in the flow oscillation generator comprising a housing, a swirl chamber with an outlet nozzle, a central body installed with a gap relative to the housing, an elastic cavity, a pressure line connected to swirl channels made in two cross-sectional planes of the swirl chamber with in the opposite swirl orientation, according to the invention, the central body is equipped with a pneumatic accumulator equipped with a flow swirl with the same swirl with the channels of the second plane bone and fluidly communicating through the gap with the disk-shaped cam twist to the first plane with the outlet nozzle, wherein the second plane twisting channels formed on a lower consumption with respect to the first plane twist channels, and an elastic cavity mounted below the outlet nozzle.

The flow tightener can be made screw or in the form of tangential channels, as well as in the form of a combination thereof, for example, in the form of a screw with tangential channels placed inside the turns.

The pneumatic accumulator can be made in the form of a cylindrical cavity with gas between the tube body and the terminated elastic hose equipped with a central perforated tube. In addition, the pneumatic accumulator can be equipped with a bypass check valve installed between the flow tightener and the elastic hose.

To improve the properties and mechanical protection, it is rational to equip the elastic cavity with a perforated casing and fill it with non-condensable gas from the group comprising nitrogen, methane, exhaust gases of internal combustion engines, air or their mixture, the volume of which does not exceed the volume of gas in the pneumatic accumulator.

If it is necessary to install relaxation flow oscillations (hereinafter referred to as the generator) below the low-frequency generator on the packer tubes during two-packer arrangement or any devices and devices, it is advisable to place the elastic cavity inside the perforated nozzle with a length of not more than 0.1 wavelength of the main harmonic component of the generated oscillations.

The generator can be installed on tubing or flexible pipes, with the most optimal input pressure line for supplying a working fluid to connect to a volumetric pump.

The generator, using swirling flows, implements the principle of generating relaxation-type self-oscillations, the most reliable when changing the load and parameters of the energy source, which makes it relatively easy to configure to excite self-oscillations in a wide frequency range and essentially consists of the phases of energy accumulation from the source and its release into the load. A mechanical analogue of this principle, for example, is the basis for the sound of stringed musical instruments.

The technical result of the proposed technical solution is achieved through an integrated approach to achieving maximum efficiency in generating relaxation flow self-oscillations, the main points of which are the rational use of the properties of swirling flows, improving their interaction, equipping a pneumatic accumulator with a fluid flow swirl synchronized with the swirling flow of the first stage.

Due to the presence of a disk-shaped swirling chamber, whose height is significantly less than its diameter (5-10 times), the energy of the jets from the swirl channels of the 1st plane is used to the maximum to form a flat swirling flow, and accordingly, a greater radial gradient of static pressure is created due to centrifugal forces . A flat swirling flow has increased resistance to external radial influences with a certain sensitivity to axial disturbances, exhibits the property of a hydrodynamic locking device that does not have movable mechanical elements, has less mass and friction and inertia losses, and, accordingly, high speed. In contrast, the prototype uses a liquid vortex, in which, based on the meaning of the word “vortex”, three-dimensional movement of elementary volumes of fluid particles takes place and their velocity, along with the tangential and radial components, also has a significant axial component and, therefore, the corresponding fraction is irrational used amount of movement obtained from the pressure line. In addition, unlike the prototype, in which the generation process is based on the amplification of pressure fluctuations in the cavity with adjustable elasticity, the present invention specifically uses a pneumatic accumulator specifically for energy storage and even conditions are especially provided for increasing the efficiency of accumulation and control of the process of generating flow fluctuations by it. Providing the central body with a pneumatic accumulator in combination with a flow swirl, with the same swirl relative to the channels of the second plane, allows to obtain a new quality, namely, to initiate relaxation auto-oscillations of the flow rate, reduce the influence of borehole conditions on the generator’s operability, and provide oscillation generation over a wide range of supply costs at acceptable supply pressures working fluid, it is rational to use the overall space inside the generator. When energy consumption is smaller compared with the prototype, by increasing the amplitude of the vibrations, a greater depth of impact on the formation, the possibility of processing deeper wells, including horizontal and sidetracks, is provided.

An analysis of the technical solutions selected during the search for information showed that there are no objects in science and technology that are similar in the claimed combination of essential features and the presence of similar technical results, which allows us to conclude that the claimed downhole equipment and generator meet the criteria of “novelty” and “inventive step” .

In FIG. 1 schematically depicts downhole equipment for processing the bottom-hole zone of a reservoir;

in FIG. 2 shows an embodiment of a hydromechanical emitter of elastic vibrations;

in FIG. 3 shows an embodiment of a hydro-pulse vibration source;

in FIG. 4 shows an embodiment of a jet pump;

in FIG. 5 shows an embodiment of a relay valve;

in FIG. 6 shows an embodiment of a mechanical source of elastic vibrations;

in FIG. 7 shows a generator of relaxation flow self-oscillations.

In FIG. 1 schematically depicts downhole equipment for processing a bottomhole formation zone. The equipment contains a jet pump 1 with a non-return nozzle valve 2 and a hydraulic accumulator 3 located above the packer 4, mounted under the packer of a valve-relay 5 with a non-return hydraulic valve 6, as well as a hydromechanical emitter of elastic vibrations 7, a generator of low-frequency self-sustained oscillations of flow rate 8 in an embodiment of an elastic cavity 9 between the suspension springs of the spring-loaded centralizer 10.

The equipment is lowered into the well on tubing 11 and 12 inside the casing 13 so that the generator and hydromechanical emitter are located in the interval of the reservoir. At the mouth, fittings with a central valve B1 and an annular valve B2 are installed. For convenience, it is rational to use a block of valves B3, B4, B5 and B6, to which a pump unit 14 and a drain line with a cyclone separator 15 are connected, fixed in the process tank 16 on the opposite side from the intake of the pump unit. The cyclone separator serves to separate the gas, as a quencher of the flow energy during oil and gas manifestations, and also to reduce the drilling of the working fluid in order to provide a more calm deposition of suspended particles carried out from the formation to the bottom of the process tank 16.

The process of treatment of the bottom-hole zone of the formation includes 2 main stages of the downhole equipment - wave action and depression. If necessary, additional stages can be performed, for example, heat exposure, injection of reagents with various functional purposes, as well as operations on repression, depression, repression and other influences on the bottomhole formation zone.

Downhole equipment for processing bottom-hole formation zone is as follows.

In the stage of wave action on the reservoir with the unpacked packer (without packer landing), the central valve B1, the annular valve B2, valves B3 and B4 are opened, and valves B5 and B6 are closed. The pump unit 14 through the valves B3 and B1 in the tubing 11 pump the working fluid, which passes through the diffuser 17 and the mixing chamber 18 of the jet pump 1. The check valve 2 is closed and the working fluid bypassing the nozzle 19 passes into the receiving chamber 20, from it through the connecting channels 21 through the trunk of the packer 4, the direct-flow channel 22 of the valve-relay 5 and the non-return valve 6, the axial channel of the hydromechanical emitter 7 enters the generator 8 with an elastic cavity 9, through which flow oscillations are excited, transmitted through the perforation e and holes in the layer are transformed into elastic oscillations. Simultaneously with the generator, a hydromechanical emitter of elastic vibrations is working 7. Then, the liquid exiting the generator moves up the annular space bypassing the unpacked packer 4 between the casing 13 and tubing 12 and 11 and through valves B2, B4 and the separator 15 is discharged into the technological tank 16, from where the settled working fluid is taken by the pumping unit and pumped into the tubing 11, that is, the so-called direct circular circulation mode is maintained.

At the outlet of the diffuser, it is advisable to install a flow swirl 23, which can be made in the form of a twisted plate, screw, impeller, etc. When the fluid moves from the tubing into the diffuser 17 in a swirling flow, the peripheral speed increases as the diameter narrows. In it, phenomena similar to those occurring in cyclone-type separators arise. Suspended particles in the working fluid, which did not have time to settle in the process vessel, are pressed against the diffuser wall, then to the mixing chamber 18, to its confuser and bypassing the nozzle 19 into the receiving chamber 20. This prevents nozzle chamber 24 from clogging and ensures normal the operation of valve 2, since in the stage of depressive effect it will be necessary to supply the working fluid through the channel of the active fluid 25. During the reverse movement of the fluid, when the jet pump is turned on and the fluid from the diffuser 17 exits IT in the tubing 11, then the flow is strongly turbulent. Thanks to the twist using a twist 23, the stream orders the movement of fluid in the tubing. With moderate twisting of the fluid, the friction on the pipe wall is not significant, but the velocity profile along the pipe cross section is leveled and the tubing throughput increases accordingly. All this leads to a decrease in pressure losses and increase the efficiency of the jet pump.

A distinctive feature of the hydrodynamic generator of relaxation flow self-oscillations is that pressure pulsations are created inside the pipes above the generator against the background of stationary pressure, which occurs during the generator’s operation due to the formation of a pressure drop relative to the bottomhole pressure during the flow of the working fluid through the tangential openings, i.e. flow. The frequency of these pulsations is equal to twice the fundamental frequency of the generated oscillations in accordance with the phases of energy storage from the source and its release to the load. Using a hydromechanical emitter 7, these pressure pulsations are converted into force vibrations on the casing and transmitted to the formation in the form of elastic vibrations.

In FIG. 2 shows an embodiment of a hydromechanical emitter (GMI). It includes a housing 26 with an axial channel 27 hydraulically connected through openings 28 with at least three cylinders radially located in the housing, in which pistons 30 are sealed with sealing rings 29, having the shape of concentrators 31 in the form of truncated cones on the outside with a contact area of a larger area of perforations, while on the side of the axial channel and on the outside of the housing, limiters 32 for piston movement are made, and the pistons themselves are equipped with return springs 33.

Under the action of stationary pressure in the axial channel 27, the movable rigid pistons are pressed against the casing, and pressure pulsations acting on the inner surface of the pistons 30 create variable AF forces proportional to the product of their area S and the amplitude of the pressure pulsations ΔΡ, i.e., A ** F = ** P * S. Due to the execution of the outer side of the pistons in the form of concentrators 31, an increase in the force on the column is achieved in proportion to the ratio of the areas of the inner and outer contact surfaces and, accordingly, the amplitude of the elastic vibrations emitted into the formation increases. The implementation of the contact area with the casing larger than the area of the perforations prevents the probable entry of concentrators into the perforation channels and the occurrence of an emergency.

Due to the emission of elastic vibrations into the formation through the casing using GMI, simultaneously with high-amplitude oscillations from the generator through perforation holes, the formation coverage by the wave action increases.

In complicated conditions, it is useful to include a hydro-pulse oscillation source (GIIK) in the layout of the downhole equipment. Pulsed pressure fluctuations at the bottomhole zone are created when the generator interacts with the GIIK. In FIG. 3 schematically shows an embodiment of the GIIK with a housing 34, which is located in the tubing 13 below the generator 8 with an elastic cavity 9. In the stream splitter 35, a pulse channel 36 and a channel 37 from the output of the generator are made. According to the functionality of the GIIK, it relates to direct-acting valves and is made in the form of a differential spring-loaded locking and regulating element 38 with a seat 39, which is adjusted using the adjusting springs 40 and 41, tightened with screws 42 and 43, respectively. The input channel is connected to the locking and regulating element 38 44 and output channels 45. The locking and regulating element 38 is made in the form of a cylinder having a cone 46 from the side of the saddle 39, and from the side of the spring 40, a groove 47 with spring-loaded balls 48 placed in it. -symmetric cavity 49 with the spring 40 is a ledge 50 and is brought to the cavity passageway 51. To prevent contamination of the cylindrical cavity can be retrofitted hydroprotection. To transmit oscillations from the generator and pressure pulses from the GIIK into the treatment zone, holes 52 were made in the tubing.

The inclusion of the valve in the work to create pressure pulses is associated with the operating modes of the generator 8, namely, a change in the stationary differential pressure directly on the generator, which quadratically depends on the flow rate of the fluid pumped through the generator. For controlled operation of the GIIK, it is configured for a pressure drop that exceeds the nominal pressure drop of the generator. The main force on the locking and regulating element 38 is set by the spring 40, and the additional force is achieved using a series of springs 41, supporting balls 48 to the conical side of the groove 47.

GIIK works as follows.

With a nominal pressure drop and fluid flow through the GIIK, the shut-off and control element 38 is in the closed state. When the fluid is supplied through the tubing string 13, the fluid passes through the generator 8 with an elastic cavity, the flow separator 35 and through the channel 37 and the holes 52 of the perforated nozzle in the form of flow fluctuations enters the formation treatment zone, and then is poured into the technological tank through the annulus. Only the generator works.

If necessary, connect to the operation of the GIIK to increase the flow rate of the pump. At the same time, due to the throttling of the liquid in the generator 8, the pressure drop increases, which is transmitted to the pulse channel 36 of the flow splitter 35 and acts through the input channel 44 to the differential locking-control element 38. In addition, due to the supply of the jet pump with a hydraulic accumulator 3 (see Fig. 1), in the latter the gas is additionally compressed and potential energy is accumulated. The flow rate continues to increase until the pressure drop to which the GIIK is adjusted increases. Since the locking and regulating element 38 (see Fig. 3) is made in the form of a cylinder having a cone 46 from the side of the seat 39, the pressure drop acts on a small area corresponding to the cross section of the channel in the saddle. After overcoming the force of the springs and the appearance of a gap between the cone 46 and the seat 39, that is, when the valve is opened, the pressure differential begins to act on a large area corresponding to the cross section of the cylindrical part 38, which is the differentiation of the locking-regulating element. This leads to a sharp increase in the force on the springs 40 and 41 and then to the complete opening of the GIIK. A moving column of liquid from the tubing 13 is poured out through the outlet channels 45 and a volume displaced by the compressed gas from the accumulator is added to it, which increases the pulse energy. Due to the differentiability and such a combination of efforts from the side of the springs 40 and 41 to the locking and regulating element 38, a clear opening of the pulse valve and the creation of a direct shock pressure pulse in the processing zone are ensured.

The outflow of liquid from the tubing 13 leads to a decrease in pressure over the GIIK and, under the action of the spring 40, the locking and regulating element 38 moves to the seat 39. When the balls 48 hit the conical side of the groove 47, additional force from the side of the springs 41 begins to act, which leads to the final pressing of the locking -regulating element 38 to the seat 39. In addition, the force created by the spring-loaded balls prevents the vibration of the valve when it is closed. The accumulator 3 also contributes to the accuracy of closing the GIIK (see Fig. 1), which slows down the pressure increase in the tubing 13.

After increasing the fluid pressure above the flow separator 35, the cycle is repeated and pulses of fluid pressure are periodically generated in the well treatment zone simultaneously with the operation of the generator. The operation of the valve is stopped by reducing the flow rate through the generator and, accordingly, the pressure drop to nominal values.

The impact of pressure pulses from the GIIK, simultaneously with the action of regular oscillations created by the generator and the GMI, allows you to increase the radius of the wave processing of a deeply-zapped PZP.

If necessary, close valve B2 (see Fig. 1) and pump the working fluid into the reservoir with an increase in bottomhole pressure above the reservoir to create repression (force impact), the duration of which is sufficient to accumulate a high potential supply of elastic energy for compressing the fluid and rock in the most contaminated area of the bottomhole formation zone near the well, and then open valve B2 to spout and create a local depression on the formation and immediately resume circulation. The injection and spout are cyclically repeated, thereby translational-force and hydrodynamic action is carried out. When injected into the reservoir, due to a wide range of operating costs of the generator, a pulsating flow of liquids occurs, which increases the efficiency of processing of the bottomhole formation zone. In the absence or low injectivity, the packer is packaged (planted), which allows pumping fluid, as well as reagents at elevated pressures, up to hydraulic fracturing.

After wave and force impacts, a depressive effect is produced on the formation to extract the mud or reaction products after the injection of reagents.

A jet pump is used to create depression on the formation. In FIG. 4 schematically shows an embodiment of a jet pump equipped with a hydraulic accumulator. The jet pump includes a diffuser 17 with a nozzle 53, a mixing chamber 18, a receiving chamber 20 with passive fluid supply channels 21, a nozzle 19, a nozzle chamber 24 provided with a check valve 2 with a seat 54, the lower part of which has sealing rings 55 and is installed in compensator 56 in the cylindrical cavity 57 with the possibility of telescopic movement. A hydraulic accumulator 3 is made in the lower part of the compensator 56. In the embodiment of the hydraulic accumulator 3, the mechanical strength of the hydraulic accumulator and the reliability of operation are increased in the form of a terminated elastic hose with gas located in a perforated casing. In the compensator, longitudinal through channels 58 are made, as well as radial channels 25, communicating a cylindrical cavity with the external surface of the compensator and the annulus, while a filter 59 is installed before entering the channels 25.

To create low-pressure pulses (implosion) in the interval of the reservoir, a relay valve equipped with a check valve is used. In FIG. 5 schematically shows an embodiment of a valve relay. It includes a housing 60 with a locking and regulating element 61, which is spring-loaded with the main adjusting spring 62 with a screw 63. A spring-loaded check valve 6 is made in the lower part of the housing. The locking and regulating element 61 contains conical and cylindrical parts with the possibility of its movement inside the cylindrical cavity with a spring 62. On the cylindrical part of the locking-regulating element, two grooves 64 with conical sides are made around the circumference and spring-loaded ball clips 65 with springs 66 and screws 6 are installed 7. Drain channels 68 are brought to the locking-regulating element. Drainage channels 69 are connected to the cylindrical cavity with the main spring 62. A saddle 70 is installed in the lower part of the cylindrical cavity, on which the conical part of the locking-regulating element 61 sits. In the housing 60 in the expanded and the sealed part is made direct-flow channels 22, as well as supply channels 71.

In the depressive stage, the packer is packaged (planted). Valves B3 and B4 are closed, and valves B1, B2, B5 and B6 are opened (see Fig. 1). The pump unit 14 through the valves B6 and B2 into the annular space pumped working fluid, which starts the jet pump 1. From the annular working fluid through the filter 59 (see Fig. 4) and the channel of the active fluid 25 enters the cavity 57 of the compensator 56 and opens the non-return valve nozzle 2, then moves along the nozzle chamber 24 to the nozzle 19, exits the nozzle at high speed and, when moving in the receiving chamber 20, transmits an impulse of motion of the passive fluid coming through channels 21 and 58 from the tubing 12 and the under-packer space, as well as fluid flowing from the formation. In the receiving chamber, the active and passive liquids are mixed, the mixture of which passes through the mixing chamber 18 and then goes through the diffuser 17 to the tubing 11 (see Fig. 1), then to the mouth and through valves B1 and B5 and the separator 15 is discharged into the process tank 16, from where it is selected by the pumping unit and the reverse circular circulation mode is supported. At the same time, in the tubing 12 below the jet pump, the pressure below the reservoir begins to decrease, which is transmitted to the hydraulic accumulator 3 and reduces the volume of fluid in the latter due to the expansion of the gas in the elastic shell and a corresponding increase in its volume. The flow of liquid from the bottom is prevented by a non-return valve 6, which is equipped with a valve relay 5. Since the pressure at the bottom in the under-packer space is equal to or close to the reservoir, an excess liquid pressure arises under the relay valve, which through channels 71 (see Fig. 5) and the seat 70 acts on the locking and regulating element 61. In the initial position, the locking and regulating element 61 is held by a spring 62 and spring-loaded ball clamps 65 in the grooves 64. When a certain differential pressure of the liquid reaches It is regulated by tightening the spring 62 with the screw 63 and additionally by tightening the springs 66 of the ball retainers 65 with the screws 67, the latches sharply come out of the upper groove. Due to the additional pressure difference associated with the relay actuation of the clamps, the shut-off and control element 61 moves sharply to the upper position, the valve-relay opens and through the generator, supply channels 71 and drain channels 68, the liquid from the bottom rushes to the jet pump. The latches 65 jump into the lower groove. At the bottom due to a sharp decrease in bottomhole pressure, an implosion impulse is created. Like gas in implosers with a rupture of membranes in the accumulator, the gas begins to compress and, together with pumping the liquid out with the jet pump, accelerates the liquid in the tubing, which leads to water hammer under the jet pump, which is reflected from the jet pump with the accumulator and transferred back to the bottom and acts on the reservoir in the form of an impulse of increased pressure (see the book Popov AA Impact effects on the bottomhole zone of wells. - M .: Nedra, 1990. - 138 p.). Without a hydraulic accumulator, the combination of a jet pump with valves is not able to create any significant impulse pressures, since the working fluid is very incompressible and there are no conditions for accelerating the flow and acquiring it at a significant speed to create a hydraulic shock.

In the upper position, the locking and regulating element is held by the same clips 65 until the pressure drop of the liquid drops to a certain value, depending on the tightening of the spring 66 of the clips. Due to the inertia and relay response of the clamps, the retention time of the valve-relay in the open state is significantly longer than the duration of the implosion pulse and the reverse pulse of increased pressure, therefore, the jet pump manages to pump out a sufficient volume of liquid from the bottom and reduce the pressure below the reservoir. After that, the differential valve under the action of the spring 62 abruptly returns to its original lower position, cutting off the liquid under the relay valve. After processing and stopping the pumping unit, the pressure in the annulus through the check valve with a slightly preloaded spring is transferred to the under-packer zone, which is essential to reduce the force on the packer when it is unpacked when lifting the equipment.

To increase the acceleration of the fluid, it is advisable to install the generator in the saddle, then when the flow increases sharply when the relay valve is opened, the generator will jump out of the saddle and will not interfere with the fluid movement. Due to the creation of implosive and hydroshock pulses of pressure in the liquid at the bottom, the combination of a jet pump equipped with a hydraulic accumulator and a periodically activated relay valve equipped with a non-return valve allows elastic oscillations to be excited in the formation and, at the same time, unlike well-known implosers, to produce long-term pumping of the formation fluid from the bottomhole formation zone, which dramatically increases the recovery efficiency of colmatant and reaction products after chemical treatment of the formation. This reveals a new, unknown from the prior art, non-obvious technical solution, which has a significant difference from identical solutions.

To carry out the depressive-repressive action, the central valve B1 is closed (see Fig. 1) and at pressures not exceeding the maximum allowable on the casing or formation, injection is made through the annulus of the working fluid, which enters through the nozzle valve 2 into the nozzle 19, further into the receiving chamber 20 and the connecting channels 21, through the trunk of the packer 4, the hydraulic valve 6 and the generator are pumped into the reservoir (repression). Then open valve B1 and immediately resume the operation of the pump unit in the calculated mode (depressive effect). Then, the same actions are carried out several times.

The design and geometrical parameters of the main flow channels of the jet pump nozzle, mixing chamber, diffuser, and receiving chamber (see Fig. 3) are optimized to reduce hydraulic losses, increase strength, operational reliability and ease of maintenance, ensure the operation of the generator and depression and repression on the PPP. This is achieved by supplying the nozzle chamber of the jet pump with a check valve, the lower part of which has sealing rings and is installed in the compensator in a cylindrical cavity with the possibility of telescopic movement, and the cylindrical cavity is communicated by channels with the outer surface of the compensator and the annular space. Due to the telescopic movement of the check valve during assembly of the jet pump, small changes in the length of the nozzle made of standard segments of tubing, as well as changes in size when making up the tapered thread, are compensated. An increase in the efficiency of the jet pump and its efficiency is achieved by installing interchangeable nozzles and a mixing chamber, the diameters of which for each particular well are calculated according to special computer programs, taking into account the necessary (or permissible) reduction of the bottomhole pressure, indicating the rational range of pressures and flow rates of the working fluid pump unit.

In special cases, it is advisable to include a mechanical source of elastic vibrations (MIUK) in the downhole equipment, which is connected with the generator. As an option, it is made in the form of a transducer of axial mechanical movements of the generator into mechanical impacts on the column and works in conjunction with the higher positioned jet pump, relay valve, and generator with an elastic cavity. MIUK includes (see Fig. 6) the housing 72, the slider 73 with the spring 74 and the adjusting nut 75, the strikers 76 with the axles 77 and the strikers 78 with the springs 79. The generator 8 installed in the saddle 80 with an elastic cavity 9 is used as a pusher , which is fixed to the slider 73.

MIUK works as follows. At the stage of depression, when a fluid is supplied to the annular space, a jet pump with a hydraulic accumulator and a relay valve come into operation, and, as described above, implosion pulses are created on the face, in which the liquid from the bottom faces rushes into the tubing 12. The generator has a limited flow rate and installed in the saddle 80, the high-speed flow lifts the generator 8 from the saddle, as well as the elastic cavity 9 and the slider 73 upward, compressing the spring 74. When moving upward, the slider 73 acts on the strikers 76, rotation located on the axes 77 and connected with the strikers 78 by the springs 79. The functioning of this mechanism is based on the patterns of movement of the links (strikers 76, 78) through a special unstable position, when passing through which energy is accumulated in the springs 79, which can give the strikers a significant impulse of force. When the strikers 76, 78 pass through an unstable position, they abruptly jump to another stable position (see Fig. 6) and hit the casing 12, creating elastic vibrations in it that radiate into the formation. After closing the relay valve, the generator 8 with the elastic cavity 9 and the slider 73 by the spring 74 return to their original position (see Fig. 6), while the strikers jump over an unstable position to their original stable position. The timing of the operation of the mechanism is adjusted by tightening the spring 74 with a nut 75. The principle of operation, simplicity and reliability of such devices will also be useful for equipping production wells with sucker rod pumps to influence the borehole zone, as well as to reduce or prevent the deposition of salts and paraffin on underground equipment.

In the aggregate operation of downhole equipment, the polyfrequency wave action on the bottomhole formation zone facilitates the rapid relaxation of mechanical stresses in the rocks around the wells, the destruction of deposits on the surface of perforation channels, the opening of natural cracks in the formation and the creation of a network of microcracks in the near-well zone, especially in carbonate reservoirs. In a porous medium, thixotropic liquefaction of clay inclusions occurs, disintegration of the clogging material, its bond with the rock is weakened, the filtration processes of cleaning pores and crack channels from natural and introduced colmatants are intensified, and the removal of clogging material into the well is facilitated. In addition, the beneficial effects of degassing liquids, multiphase filtration, and the blocking effect of small phases or emulsions are reduced. When injecting solutions of chemical reagents, their introduction into the reservoir is initiated and facilitated, and the reaction with colmatants is intensified. In the case of polyfrequency wave action on formations in order to increase oil recovery, a complex of various effects arises, associated with changes in stress-strain, fluid dynamic, and physicochemical processes that occur with the interaction of all three phases: a solid rock skeleton, liquid fluid, and gas in the reservoir under the influence of external and internal factors. A complex change in the state of the reservoir is expressed in the form of surface physicochemical, volumetric, and mechanical interactions of all phases, as well as the formation of abnormally initiated zones. Dilatation, phase-exchange and other processes are developing.

The hydrodynamic generator of relaxation flow self-oscillations (see Fig. 7) contains the twisting chamber housing 81 installed in the tubing 12 with an output nozzle 82 and tangential swirl channels of the 1st 83 and 2nd 84 planes, a central body 85 equipped with a pneumatic accumulator 86 with a flow swirl 87, the elastic cavity 9. The central body is installed in the body of the swirl chamber with a gap 88 relative to the wall, and from the nozzle side with the formation of a disk-shaped swirl chamber 89. Moreover, as an optimal option, pneumohydroaccumulate p is configured as a cylindrical cavity with a gas between the tubular body and terminated with a flexible hose fitted with a central perforated tube; the twist channels 84 of the second plane are made with a lower throughput than the twist channels 83 of the first plane, and the flow swirl is made in the form of tangential channels with the same twist with the channels of the second plane.

The generator operates as follows. The process of generating relaxation flow self-oscillations consists of 2 main phases: energy storage from a source, which is a pump unit that transfers energy in the form of a flow of a working fluid under pressure, and then releasing the stored energy into a load, that is, into the fluid under the generator, and through it to the PZP. In the first phase, the liquid from the pump unit along the pressure line, which is the tubing 12, enters through the twist channels of the 1st 83 and 2nd 84 planes into the body of the swirl chamber 81. In this case, in the disk-shaped swirl chamber 89 in the rotating the mass of the fluid of the 1st plane, centrifugal mass forces arise and a radial gradient of static pressure is formed, which depends on the intensity of rotation. As a result, an excess pressure is created at the periphery with respect to the axial pressure. From the swirl channels 84 of the second plane, the fluid enters the gap 88 between the central body 85 and the body of the swirl chamber 81 with a lower flow rate relative to the swirl channels 83 of the first plane, so the centrifugal mass forces are much weaker than in the swirl flow of the 1st plane. Under the action of excess pressure from the side of the swirling flow of the 1st plane, the liquid of the 2nd plane is directed through the flow swirl 87 into the pneumatic accumulator 86. Accumulation of the energy of the fluid flow in the pneumatic accumulator 86 in the form of an accumulation of liquid volume and increase in pressure continues until the pressure in the pneumatic accumulator 86 is reached equal to the excess pressure created by centrifugal forces in the swirling flow of the 1st plane in the disk-shaped swirling chamber 89. It is noteworthy that in second phase the pressure pulse generator under the reduction due to the liquid channel direction of twist 1st plane inside the generator and formation of the swirling flow axis zone of reduced pressure.

In the second phase, a change in the direction of fluid flow occurs. Since the pressure at the inlet to the swirl channels of both planes is the same, and the fluid cannot reach the pneumohydroaccumulator, the fluid starts moving from the swirl channels of the 2nd plane 84 toward the outlet of the generator, where the pressure is less. Interaction and energy exchange occur between oppositely swirling flows, as a result of which the rotational speed in the swirling flow of the 1st plane in swirling chamber 89 decreases and, accordingly, the radial gradient of static pressure created by centrifugal forces changes. The centrifugal forces in the swirl chamber 89 of the swirling flow of the 1st plane are no longer able to hold the pressure in the pneumatic accumulator, the hydrodynamic locking and regulating device opens and the accumulated energy is released from the pneumatic accumulator 86 in the form of an increasing flow, to which is added the flow from the channels of the 2nd plane 84. Although, due to the opposite twist of the channels of the 1st and 2nd planes, the energy exchange process is enhanced, but, due to the lower consumption of the channels of the 2nd plane and the longitudinal movement Nia across the gap between the central body and twisting the camera body, the rotational speed of weakening. To increase the intensity of rotation serves as a curler 87 of the moving flow from the pneumatic accumulator. Without a twist with the same swirl with channels of the 2nd plane, the longitudinal movement of fluid from the pneumatic accumulator 86 past the channels of the 2nd plane 84 would significantly weaken the swirling flow created by the channels, which would only lead to a partial opening of the hydrodynamic locking-regulating device. Due to the pneumatic accumulator 86 with a tightener 87, the counter-moments of the amount of rotational movement are amplified due to the twist, the flow of the resulting output stream becomes close to the gradient with minimal resistance for the fluid to flow out of the nozzle 82, as a result of which the energy is released in an avalanche-like manner, a flow pulse characteristic of generators of relaxation self-oscillations. Upon completion of the release of accumulated energy and the pressure drop in the pneumatic accumulator 86 in a swirling flow of the 2nd plane 84, the swirl increases and stops the flow from the pneumatic accumulator 86. Following it, circulation in the disk-shaped swirl chamber 89 is quickly restored, which leads to the influx of fluid into the pneumatic accumulator 86 and increase in pressure in it with the subsequent release of energy and the establishment of a regime of self-oscillations.

To ensure the stability of the functioning of the generator with increasing static pressure in the medium to be maintained, it is necessary that the inlet of the pressure line for supplying the working fluid be connected to a volumetric pump.

Thanks to this integrated approach, a cumulative effect is formed, which is manifested in an increase in the stability of operation, a reduction in unproductive losses of energy of the fluid flow, a multiple increase in power in the pulse due to a decrease in the duration of its release, and an increase in the upper oscillation frequency. It is especially important that since the radiated acoustic power is proportional to the square of the amplitude of the oscillations and the square of the frequency, taking into account the above, the result is a progressive (to a degree) increase in the generator power [see Mogendovich E.M. Hydraulic impulse systems. L .: "Mechanical Engineering" (Leningrad. Dep.), 1977. 216 p.].

When using a working fluid containing suspended mechanical particles, for example, suspension or water contaminated with sludge, to reduce abrasive wear, the flow swirl is made screw, although its manufacture is more labor-intensive. To reduce the size by reducing the number of turns, the flow tightener is made in the form of a screw, including a multi-start one, with tangential channels placed inside the turns. Equipping the pneumatic accumulator with a bypass check valve and a screw installed between the flow tightener and the elastic hose allows the first phase to increase the duration of accumulation of fluid volume and increase pressure in the pneumatic accumulator, and in the second phase to reduce the duration of fluid outflow from it, that is, to realize a pulsed release of accumulated energy.

For the full-fledged operation of the hydrodynamic locking and regulating device, reliable and fast flow promotion is required. And if during work in the atmosphere there are no obstacles for this, then when working in a well under the conditions of the so-called "flooded stream", the liquid at the output of the generator becomes a moderator of unwinding, and most importantly, an inertial mass to return the volume of fluid accumulated in the generator. To compensate for adverse conditions, an elastic cavity 9 is used, which, due to an increase in the total elasticity at the output of the generator, provides the main swirling flow with some freedom for its unwinding and, as a whole, is part of the generator itself, interacting with a pneumatic accumulator 86. Moreover, in a certain flow range, the interaction becomes close to resonance , which, along with an increase in the amplitude, also leads to a change in the shape of the oscillations, the rms value of the ode sonar generator efficiency and radiated acoustic power.

To improve the properties, the elastic cavity can be made, in particular, in the form of a terminated elastic hose with gas, and for mechanical protection is equipped with a perforated casing (see Fig. 7, item 9). With its volume not exceeding the volume of gas in the pneumatic accumulator, the frequency spectrum of oscillations is less depleted in high-frequency harmonics.

If it is necessary to install below the generator on the packer pipes with a two-packer arrangement or any instruments and devices, the elastic cavity can be placed inside the perforated nozzle with a length of not more than 0.1 wavelength of the main harmonic component of the generated oscillations. This length of the perforated nozzle provides a quasi-stationary process of transmitting flow fluctuations from the generator to the nozzle, and from it to the formation.

The proposed generator, due to the principle of operation incorporated into it, can successfully function when using both liquids and steam as a working fluid, as well as a mixture of liquids with powder materials (suspensions), gases (foam systems) or immiscible liquids (emulsions), which expands the scope.

To ensure optimal operation, the generators are pre-configured before working in a particular well, taking into account a number of conditions, for example, the type of working fluid, well design, tubing size, reservoir and bottomhole pressures. Owing to the design of the generator made in this way, the generation of self-oscillations is optimized, and it is possible to run generators with reduced pressure losses at sufficiently high oscillation amplitudes and acceptable dimensions. At the same time, a high hydroacoustic efficiency is achieved, and in the absence of moving mechanical components, the generator has increased reliability and motor resource. In addition, relaxation self-oscillations are inherent in specific properties, namely, a pulse-like form of vibration, which is characterized by a broadband frequency spectrum, which was confirmed by bench studies. Along with the main low-frequency (15-300 Hz) components, the spectrum contains both medium (300-1000 Hz) and high-frequency harmonics (1000-5000 Hz). Along with this, in the joint operation of the generator with GMI, GIIK and MIUK, a polyfrequency effect is carried out in a wide frequency range. And this is especially important for productive formations as a multicomponent and multiphase system, where there are a lot of effects and processes that are frequency-dependent on the effects of elastic vibrations and accordingly react when there are “natural” frequencies in the vibration spectrum.

To perform a wide range of tasks related to the processing of PPP, for example, to develop after drilling, increase productivity and resuscitate wells under various geological and physical conditions for the development of oil or gas fields, the technical condition of wells, generators of various capacities can be created with costs from units to tens of cubic decimeters per second. For this, the authors have a computer program for the engineering calculation of generators and a number of generators have been created with costs of 2-15 dm ³ / s. Choosing the power of the generators, it is possible to produce a gentle or rather rigid wave action. For example, weakly cemented sandstones require gentle action and, accordingly, low-flow generators, and for hydraulic fracturing of terrigenous strata, composed of clayey siltstone, or carbonate strata, a rigid wave action and a sufficiently large flow rate are necessary. At reduced reservoir pressures, it is advisable to use generators in conditions of depressions created by jet pumps operating simultaneously with generators or alternately. Low-flow generators with flow rates of 2-4 dm ³ / s, made in the form of small-sized nozzle generators, sufficiently satisfy the conditions for processing PPP in wells using flexible pipes (coiled tubing), to which they are attached using an adapter rolled at the end with flexible pipes (for the implementation of coiled tubing wave technologies).

In the described set of downhole equipment operation, a complex of effects and phenomena is manifested that contribute to the cleaning of the bottomhole formation zone and increase the permeability of the near-wellbore zone, as a result of which the well productivity is increased, the inflow (injectivity) profile is leveled, non-mastered or blocked interlayers of a layered-heterogeneous reservoir are connected to the work. All PPP processing operations are carried out for a single descent and lifting of equipment, and by increasing the efficiency for its operation it is not necessary to attract significant capacities of wellhead pumping units to create high pressures and flow rates, which allows to reduce the cost of processing.

The use of the invention and the industrial applicability of downhole equipment is confirmed by the popularity of functionally identical devices. The device passed bench tests and industrial testing when processing the bottom-hole zone of wells with a positive result.

Claims (19)

1. Downhole equipment for multi-frequency wave processing of the bottom-hole zone of the reservoir, including a jet pump with a nozzle chamber, a relay valve, a flow oscillator under the packer on the pipe string at the level of the perforation interval, characterized in that it is equipped with a hydromechanical emitter of elastic vibrations installed in the interval of the reservoir above the input channels of the generator, the jet pump is equipped with a hydraulic accumulator, the relay valve is equipped with a check valve and is installed below the jet pump, and the generator ying a hydrodynamic flow generator relaxation oscillations. 2. Downhole equipment for multifrequency wave processing of the bottom-hole zone of the reservoir according to claim 1, characterized in that the hydromechanical emitter of elastic vibrations is made in the form of a transducer of pressure fluctuations of the working fluid into mechanical vibrations of moving rigid elements for transmitting vibrations through the perforated production string into the formation. 3. Downhole equipment for multifrequency wave processing of the bottom-hole zone of the reservoir according to claim 2, characterized in that the transducer of pressure fluctuations of the working fluid into mechanical vibrations is made in the form of a body with an axial channel hydraulically connected to at least three cylinders radially located in the body with hermetically sealed installed pistons in which the outer side is in the form of concentrators with a contact area greater than the area of the perforation holes, while on the side of the axial channel and The body pistons are equipped with piston movement limiters, and the pistons themselves are equipped with return springs. 4. Downhole equipment for multi-frequency wave processing of the bottom-hole zone of the reservoir according to claim 1, characterized in that the valve-relay is made in the form of a housing with radial drain channels and spring-loaded ball retainers, as well as with a cylindrical cavity located along the axis of the housing with a saddle mounted in its lower part, a spring-loaded locking-regulating element and a non-return valve, which are respectively connected with the supply and direct-flow channels, the locking-regulating element contains a conical and the cylindrical part with the possibility of its movement inside the cylindrical cavity, moreover, on the cylindrical part of the locking-regulating element, at least two grooves with conical sides are made around the circumference, while in the initial position of the locking-regulating element, the retainer balls are located in the groove far from the saddle. 5. Downhole equipment for multi-frequency wave processing of the bottom-hole zone of the reservoir according to claim 1, characterized in that the accumulator is made in the form of a terminated elastic hose with gas located in a perforated casing. 6. Downhole equipment for multi-frequency wave processing of the bottom-hole zone of the reservoir according to claim 1, characterized in that the nozzle chamber of the jet pump is equipped with a check valve, the lower cylindrical part of which has sealing rings and is installed in the cylindrical cavity of the compensator with the possibility of telescopic movement, while the cavity is communicated by channels with the external surface of the compensator and the annulus, and a filter is installed in front of the channels. 7. Downhole equipment for multi-frequency wave processing of the bottom-hole zone of the reservoir according to claim 1, characterized in that a flow swirl is installed at the outlet of the jet pump. 8. Downhole equipment for multi-frequency wave processing of the bottom-hole zone of the reservoir according to any one of paragraphs. 1-7, characterized in that it is additionally equipped with a hydro-pulse source of oscillations hydraulically connected to a hydrodynamic generator of relaxation self-oscillations of the flow. 9. Downhole equipment for multi-frequency wave processing of the bottom-hole zone of the reservoir according to any one of paragraphs. 1-7, characterized in that the hydrodynamic generator of relaxation flow oscillations is mounted in the saddle. 10. Downhole equipment for multi-frequency wave processing of the bottom-hole zone of the reservoir according to claim 9, characterized in that it is additionally equipped with a mechanical source of elastic vibrations, which is mechanically connected to the generator and made in the form of a transducer of axial displacements of a hydrodynamic generator of relaxation oscillations of flow into mechanical impacts column. 11. Hydrodynamic generator of relaxing flow oscillations, including a housing, a swirl chamber with an outlet nozzle, a central body installed with a gap relative to the housing, an elastic cavity, a pressure line connected to swirl channels made in two planes of a cross-section of the swirl chamber with a mutually opposite swirl orientation, characterized in that the central body is equipped with a pneumatic accumulator equipped with a flow swirler with the same swirl with channels of the second plane and hydraulically communicating through a gap with a disk-shaped swirling chamber of the first plane with the output nozzle, while the swirling channels of the second plane are made with the possibility of passing a smaller fluid flow than through the swirling channels of the first plane, and the elastic cavity is installed below the outlet nozzle. 12. The hydrodynamic generator of relaxation flow self-oscillations according to claim 11, characterized in that the flow swirl is made in the form of tangential channels. 13. The hydrodynamic generator of relaxation flow self-oscillations according to claim 11, characterized in that the flow swirl is made in the form of screw channels. 14. The hydrodynamic generator of relaxation flow oscillations according to claim 11, characterized in that the flow swirl is made in the form of a screw with tangential channels placed inside the turns. 15. The hydrodynamic generator of relaxation flow oscillations according to claim 11, characterized in that the pneumatic accumulator is made in the form of a cylindrical cavity with gas between the tube body and the terminated elastic hose equipped with a central perforated tube. 16. The hydrodynamic generator of relaxation flow self-oscillations according to claim 11, characterized in that the pneumatic accumulator is equipped with a bypass check valve and an auger installed between the flow tightener and the elastic hose. 17. The hydrodynamic generator of relaxation flow self-oscillations according to claim 11, characterized in that the elastic cavity is equipped with a perforated casing and is filled with non-condensable gas from the group comprising nitrogen, methane, oxygen-depleted air or mixtures thereof, the volume of which does not exceed the volume of gas in the pneumatic accumulator. 18. The hydrodynamic generator of relaxation flow self-oscillations according to claim 11, characterized in that the elastic cavity is located inside the perforated nozzle with a length of not more than 0.1 wavelength of the main harmonic component of the generated oscillations. 19. Hydrodynamic generator of relaxation flow oscillations according to any one of paragraphs. 11-18, characterized in that it is installed on tubing or flexible pipes, and the inlet of the pressure line for supplying the working fluid is connected to a volumetric pump.

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