RU2774463C1 - Two-way hydraulic drilling jar - Google Patents

Abstract

FIELD: petroleum industry.

SUBSTANCE: invention relates to apparatuses for releasing a stuck part of the drill string in a petroleum borehole. The apparatus comprises a tubular body and a hollow shaft, connected telescopically. The shaft comprises, on the side of the fluid inlet, a first piston with a seal, strikers between the anvil protrusions; on the side of the fluid outlet, a second piston with a seal, forming a working fluid-filled chamber, and also comprises two limiting mechanisms for communication of fluid with the fluid chamber, each made in the form of a hollow shaft thickening, as well as a first and a second annular valves, each installed in the working fluid chamber with a shaft passing through the inner cavity. The inner surface of each annular valve is tightly adjacent to the hollow shaft thickening. A valve apparatus is installed in each annular valve, limiting the flow of fluid inside the working fluid chamber in one direction, and the first valve apparatus of the first annular valve is positioned so as to limit the flow of fluid in the opposite direction relative to the flow of fluid in the second valve apparatus of the second annular valve, and also comprises a valve body, placed wherein are a valve seat, a spacer sleeve, a first and a second annular valves. The valve body is fastened to parts of the tubular body, installed wherein are a first piston with a seal and a second piston with a seal, the above valve apparatus is installed in each annular valve, limiting the flow of fluid inside the working fluid chamber in one direction, and the first valve apparatus of the first annular valve is positioned so as to limit the flow of fluid in the opposite direction relative to the flow of fluid in the second valve apparatus of the second annular valve. A lower throttle apparatus is installed in the first annular valve, limiting the flow of the working fluid in one direction with the first valve apparatus from the working fluid chamber formed by the second piston with a seal located on the side of output of the fluid medium from the shaft, the inner surface of the first annular valve tightly adjacent to the hollow shaft thickening and the end of the annular valve tightly adjacent to the end of the valve seat, and an upper throttle apparatus is installed in the second annular valve located on the side of output of the fluid medium from the shaft, limiting the flow of the working fluid in the same direction as the second valve apparatus from the working fluid chamber formed by the first piston with a seal located on the side of intake of the fluid medium into the hollow shaft, the inner surface of the second annular valve tightly adjacent to the high-diameter belt of the hollow shaft and the end of said annular valve tightly adjacent to the end of the part of the tubular body directed thereto.

EFFECT: operating life and reliability are increased, ultra-high impact strength in the wellbore is provided with the optimal ratio between the impact load and impact pulse, accuracy of delay time created by the hydraulics is increased, reliability of release of the drill string from sticking is increased.

3 cl, 2 tbl, 7 dwg

Description

The invention relates to devices for applying upward and/or downward shock loads to release a stuck portion of a drill string in an oil well by responding to a longitudinal force applied to the drill string and jar.

Known mechanism of the double-acting hydraulic jar, including parts of the outer element (2, 4, 9, 10, 14, 17), parts of the inner element (1, 5, 11), fixed on the outer element (2, 4, 9, 10, 14 , 17), a working fluid chamber (35, 37, 42) divided by parts of the inner element (1, 5, 11) and the outer element (2, 4, 9, 10, 14, 17), and the limiting mechanism (12, 13 , 48, 50) liquid communication with the liquid chamber (35, 37, 42), while the internal (1, 5, 11) and external elements of the housing (2, 4, 9, 10, 14, 17), movable relative to each other other between the first design, in which the limiting mechanism (12, 13, 48, 50) limits the relative movement between the internal (1, 5, 11) and external elements of the housing (2, 4, 9, 10, 14, 17), and the second a design in which the limiting mechanism (12, 13, 48, 50) limits the relative movement between the internal (1, 5, 11) and external elements of the housing (2, 4, 9, 10, 14, 17) to a lesser extent than in the first design, and the limiting mechanism contains two valve devices (58), each of which limits the movement of fluid inside the chamber (35, 37, 42) in one direction, while the valve devices (58) are located in such a way as to limit the movement of fluid in opposite directions (GB 2332921 A, 07.07.1999).

The disadvantage of the known design is the insufficient resource of the seal 38 of the inner element 11 and the seal 40 of the inner element 15, which, when moving relative to the outer elements of the housing 9 and 14, respectively, form chambers 35 and 42, respectively, for the working fluid (oil) under pressure, for example, 130÷ 150 MPa.

As a result, oil leaks under pressure, for example, 130÷150 MPa from chamber 35 into the cavity for oil and splined shaft 22, and oil leaks under pressure 130÷150 MPa from chamber 42 into the cavity of parts of internal elements (1, 5, 11), filled with a drilling fluid containing solid abrasive particles, for example, up to 2% sand with dimensions of 0.15 ÷ 0.95 mm and up to 5% oil products of polymer clay drilling fluid with a density of 1.16 ÷ 4.26 g/cm ³ pumped at hydrostatic pressure, for example, 25÷40 MPa.

Another disadvantage of the known design is the insufficient resource of the spring-loaded latch mechanism (5, 8), which includes the first element (8) of the latch located on the inner element (1, 5, 11) or on the outer element of the housing (2, 4, 9, 14, 17), and the second element of the latch (5) on one of the elements of the housing, adjusted to fix the elements of the housing together, for example, due to wear of the teeth during operation, the release force from the lock decreases, with the maximum hardness of the teeth of the latch, it is technologically difficult to provide high (maximum for steel) the strength of the teeth, with the maximum strength of the latch teeth, it is technologically difficult to provide high (maximum for steel) hardness of the teeth, when surfacing the surface layer, for example, with a hard alloy, it is technologically difficult to reduce the brittleness of the teeth and provide high (maximum for steel) impact strength of the teeth.

Another disadvantage of the known design is the incomplete use of the possibility of creating ultra-high impact power for the occurrence of shock loads directed upwards (when the drill string is tensioned) to release the drill string and (or) drilling tool in the well from sticking, which is explained by large pressure losses in the second design, in which the limiting mechanism (12, 13, 48, 50) limits the relative movement between the internal (1, 5, 11) and external elements of the housing (2, 4, 9, 10, 14, 17) to a lesser extent than in the first design , and the restricting mechanism contains two valve devices (58), each of which limits the movement of fluid inside the chamber (35, 37, 42) in one direction, while the valve devices (58) are located in such a way as to limit the movement of fluid in opposite directions.

The difficulty of controlling the load directed downwards is explained by the small longitudinal travel (not exceeding the value of the protrusions of the bands of increased diameter 13 of the mandrel 11) of the limiting mechanism (12, 13, 48, 50), which limits the relative movement between the internal (1, 5, 11) and external elements of the housing (2, 4, 9, 10, 14, 17), and a large hydraulic resistance of the second design, in which the limiting mechanism (12, 13, 48, 50), including two valve devices 58, each of which limits the movement of fluid inside the chamber (35, 37, 42) in one direction, and valve devices 58 arranged so as to restrict the movement of fluid in opposite directions.

In this case, the value of the longitudinal stroke of the annular valve, for example, 13 between the restrictive parts 53, 63 of the body parts 10, 14, is an order of magnitude less than the longitudinal stroke of the inner parts 1, 5, 11 of the mandrel 1 relative to the external elements (2, 4, 9, 10, 14, 17) body 2, determined by the spring-loaded latch mechanism, from the beginning of the application of force pushing the mandrel into the body, until the latch mechanism is set to its working position.

As a result, it does not provide an increase in the accuracy of the “lag” time created by hydraulics for striking at the optimal ratio between shock load and shock impulse, and this does not allow the operator at the rig to change the allowable force force of the drill string tension, and then apply the drawworks brake, when In this case, the sticking release force is difficult to control, which reduces the possibility of releasing a stuck drill string in the well.

A double-acting hydraulic drilling jar is known, consisting of a tubular body and a hollow mandrel, telescopically connected to each other, the tubular body is made of parts, contains a thread on the side of the first edge, in the middle part contains internal protrusions-anvils, and on the side of the second edge contains slots on internal surface and a seal, wherein the hollow mandrel is made of parts, contains the first piston with the first seal on the side of the first edge of the tubular body, the impactors located between the internal protrusions-anvils of the tubular body, on the second edge of the tubular body contains the second piston with the second seal, forming a chamber filled with a working fluid - oil, a threaded shank and slots - on the outer surface, and also containing two limiting mechanisms for communicating the fluid with the fluid chamber, each of which is made in the form of a belt of an increased diameter of a hollow mandrel, as well as the first and second annular valves, every The first of which is installed in the working fluid chamber with a hollow mandrel passing through the internal cavity, the inner surface of each annular valve is in close contact with the corresponding belt of an increased diameter of the hollow mandrel, while each annular valve has at least one valve device that limits the flow liquid inside the working fluid chamber in one direction, and the first valving device of the first annular valve is located in such a way that it restricts the flow of fluid in the opposite direction relative to the flow of fluid in the second valving device of the second annular valve, while the hydraulic jar contains a central piston equipped with its own annular seals , the central piston is formed by an annular collar of increased diameter of the hollow mandrel and is placed in the working fluid chamber formed by the inner diameter of the hollow body, the first and second annular valves and the hollow mandrel passing through without a working fluid chamber, the first valve device is installed in the first annular valve in such a way that it restricts the flow of working fluid from the chamber formed by the central piston provided with its own annular seals, the inner diameter of the hollow body, the first annular valve and a hollow mandrel passing through the working fluid chamber into the chamber formed by the first piston with the first seal on the side of the first edge of the hollow mandrel, the inner diameter of the hollow body, the first annular valve and the hollow mandrel passing through the working fluid chamber, and the second valve device is installed in the second annular valve in such a way that limits the flow of the working liquid from the chamber formed by the central piston equipped with its own ring seals, the inner diameter of the hollow body, the second annular valve and the hollow mandrel passing through the working fluid chamber into the chamber formed by the second piston with the second seal with st the crown of the second edge of the hollow mandrel, the inner diameter of the hollow body, the second annular valve and the hollow mandrel passing through the working fluid chamber (RU 2439284 C2, 10.01.2012).

The disadvantage of the known design is the incomplete possibility of increasing the life of the seal 22 of the piston 21, threaded with part 18 of the hollow mandrel 2, on the surface 57 of part 3 of the tubular body 1, which is located at the interface of the chamber 55 for liquid - oil 28 with a cavity for drilling fluid 88, which is subjected during operation to a high working fluid pressure, preferably 150 MPa, and instantaneous release of said working fluid pressure to a hydrostatic pressure level, for example, 30 MPa, of the drilling fluid 88 in the drill string.

Abrasive particles of drilling mud, for example, up to 2% sand with dimensions of 0.15÷0.95 mm and up to 5% oil products of polymer-clay drilling mud with a density of 1.16÷1.26 g/cm ³ , contaminate the oil in the fluid chamber 28 27, clog the oil filters 36 in the bypass valves 31, 32, block the flow area of the jets for oil circulation in the bypass valves 31, 32 installed in the annular valves 34, 42, while oil leaks from the fluid chamber 28 into the cavity for drilling mud 88 in the well, damage to the seal 22 by abrasive particles of the drilling mud, which does not provide an increase in service life and reliability, reduces the possibility of releasing a stuck drill string in the well from sticking.

A double-acting hydraulic drilling jar is known, containing a tubular body, a hollow shaft telescopically installed in it, having the ability to move freely in the axial direction of the body, while the shaft and the body are made of connected parts and the body parts are connected by body adapters, the first and second pistons are installed in the body , between which a chamber filled with working fluid is formed for working fluid, located between the housing and the shaft, also between the housing and the shaft a cavity is formed, with which the chokes oppositely directed in the axial direction of the jar are connected, communicated with the specified chamber, characterized in that the jar is equipped with a shaft enclosing an annular body common for the chokes, in which at least a pair of diametrically located threaded holes is made with chokes located in them oppositely directed in the axial direction, the annular body is located between the ends of the body adapters with the possibility of interacting with its internal surface with a thickening of the shaft when it moves between the ends of the adapters, as well as the possibility of interaction of its ends with the ends of the body adapters, in the wall of the annular body on its opposite end sides there are inclined holes communicated with threaded holes, communicated with the cavity formed by the body, shaft and ends adapters (RU 2726689 C1, 07/15/2020).

The disadvantage of the known double-acting hydraulic drilling jar is that during operation (during recharging) it alternately creates shocks in the up and down direction, it is impossible to create shocks in only one direction.

For a double-acting hydraulic drilling jar, the determining factor is the creation of repetitive impact loads directed in one direction, essentially only upwards, which are necessary for the occurrence of a certain level of relaxation of tensile stresses, undulating along the length of the pipe string in a deviated well, and obtaining the optimal ratio between shock load and impact impulse applied to the place of sticking of the string.

In practice, to release a stuck drill string in a well when drilling complex deviated wells with a high coefficient of friction, where it is difficult to create the axial force necessary to recharge the jar, for example, to release a drill string from stuck drill pipe in a directional well, in the drilling interval of 3500 -4500 m, drilling companies operate predominantly with allowable ("metered") drillstring tension and jar actuation by repeated upstrokes, eg 600 upstrokes and 45 downstrokes.

Closest to the claimed invention is a double-acting hydraulic drilling jar, consisting of a tubular body and a hollow shaft, telescopically connected to each other, the tubular body is made of parts, contains a thread from the first edge, in the middle part contains internal protrusions-anvils, from the second the edge contains slots on the inner surface and a seal, the hollow shaft is made of parts, contains the first piston with the first seal on the side of the first edge of the tubular body, the impactors located between the internal protrusions-anvils of the tubular body, from the second edge of the tubular body contains the second piston with the second seal , forming a chamber filled with a working fluid - oil, a threaded shank and slots - on the outer surface, and also containing two limiting mechanisms for communicating the fluid with the fluid chamber, each of which is made in the form of a belt of increased diameter of the hollow shaft, as well as the first and second to annular valves, each of which is installed in the working fluid chamber with a hollow shaft passing through the internal cavity, the inner surface of each annular valve is in close contact with the corresponding belt of an increased diameter of the hollow shaft, while at least one valve device is installed in each annular valve , limiting the flow of fluid inside the working fluid chamber in one direction, and the first valve device of the first annular valve is located in such a way that limits the flow of fluid in the opposite direction relative to the flow of fluid in the second valve device of the second annular valve, while the hydraulic drilling jar contains a valve module, comprising a valve body and a body adapter fastened together, inside the valve body there is a valve seat, a spacer sleeve, as well as the first and second annular valves mentioned above, while the valve module is fastened to parts of the tubular body ca, inside which the first piston with the first seal and, accordingly, the second piston with the second seal are installed, and at least one valve device mentioned above is installed in each annular valve, which limits the flow of fluid inside the working fluid chamber in one direction, and the first the valve device of the first annular valve is located in such a way that it limits the flow of fluid in the opposite direction relative to the flow of fluid in the second valve device of the second annular valve, and forms, with a hollow shaft passing through the internal cavity of the valve module, the central part of the chamber filled with the working fluid - oil, at the same time, the valve body is made with an internal annular belt, the end of the internal annular zone is directed towards the end of the body adapter, the spacer sleeve is installed with axial play between the first and second annular valves mentioned above, the valve seat is made with its own seal a shaft in contact with the inner surface of the valve body and installed between the end face of the inner annular belt of the valve body and the second annular valve, between the inner surface of the spacer sleeve and the outer surface of the band of increased diameter of the hollow shaft, a through annular channel is formed, between the inner surface of the valve seat and the outer surface of the band of the increased diameter of the hollow shaft, a through slotted channel is formed, the end face of the first annular valve is in close contact under the action of the pressure of the working fluid with the end face of the body adapter directed towards it, the end face of the second annular valve is in close contact under the action of the pressure of the working fluid with the end face of the valve seat directed towards it, while the parts tubular body, designed to install the first piston with the first seal and, accordingly, the second piston with the second seal, forming chambers filled with working fluid with parts of the hollow shaft, made with a smooth stepped cavity (RU 2521993 C1, 07/10/2014).

The disadvantage of the known double-acting hydraulic jar is the incomplete possibility of increasing its resource and reliability, the formation of ultra-high shock power in the wellbore with an optimal ratio between the shock load and the shock impulse acting up and down on the drill string sticking point, as well as the incomplete possibility of providing hydraulic delay time bypass valves during the assembly and testing of the hydraulic jar, and as part of the drill string - an incomplete possibility of increasing the reliability of releasing the drill string from sticking in the well when drilling complex deviated wells with a high coefficient of friction, where it is difficult to create the axial force necessary for reloading the jar, mainly for work with an allowable ("metered") tension force of the drill string and actuation of the jar by repeated blows only upwards.

Another disadvantage of the known double-acting hydraulic jar is the incomplete use of the ability to control the dynamics of the pressure release of the working fluid from the high pressure chamber, mainly 150 MPa, and the instantaneous discharge of the specified high pressure of the working fluid to a pressure level, for example 30 MPa, into the damping chamber when creating shock loads, directed upwards, necessary for the occurrence of a certain level of relaxation of tensile stresses, moving in waves along the length of the pipe string in the well, obtaining the optimal ratio between the shock load and the shock impulse applied to the place of sticking of the string.

The disadvantage of the known double-acting hydraulic jar - the incomplete possibility of providing the hydraulic delay time of the bypass valves during the operation of the hydraulic jar, is explained by the "sliming" of metal microparticles due to wear and chipping of rubbing surfaces - chromium coating layers in friction pairs, which causes clogging of the filters of the said bypass valves.

As a result, the required delay time created by hydraulics is not provided for applying repeated upward blows, with an optimal ratio between shock load and shock impulse, and this does not allow the operator at the rig to change the allowable tension force of the drill string, and then apply the drawworks brake, while the force when releasing the sticking is difficult to control, as a result, the possibility of releasing the drill string from the sticking in the well is incomplete.

Bypass valves for hydraulic jars, US Pat. No. 5,123,493, Jum. 23, 1992, Valve used in a hydraulic drilling jar, Inventors: Wenzel; Kenneth H. (Edmonton, Alberta, CA), manufactured for drilling companies, principally by The Lee Company (US) under the trademark Lee Visco Jet, p. 42, Lee JEVA, www.TheLeeCo.com.

Known hydraulic jars company "Radius-Service" (RU), which is part of the "Schlumberger" (US), for example, RU 2544352 C2, RU 2540372 C2, RU 2521993 C1, RU 2537722 C2, RU 2439284 C2 (park 900 units) , which have been reliably operating in wells in Russia and abroad for more than 10 years, using bypass valves from The Lee Company (US), Lee Visco Jet, p. 42, Lee JEVA, www.TheLeeCo.com.

When the operating time reaches 750 hours from the moment of commissioning or after the last repair, the jar is taken out for repair. Under normal operating conditions, the total number of strokes of the jar prior to repair (revision) should not exceed 800.

Possible causes of hydraulic jar failures.

- Hydraulic jar not working, possible causes: Stuck drill string above the jar. The failure of the hydraulic jar is due to its incorrect placement in the drill string.

- The time required for the flow in the jar of the working fluid is not maintained (hydraulic "delay").

- When carrying out a blow directed downward, the tensile load acting on the hydraulic jar during the circulation of the drilling fluid-drilling mud (load from the operation of the mud pump) is not taken into account. Failure of the hydraulic jar is associated with insufficient unloading of the drill string or the weight of the drill string over the jar is insufficient to apply the required compressive force.

- The hydraulic jar worked but then stopped working, possible reasons:

After the impact, they did not reload the jar. During jar recharging, sections of the well with possible complications (screes, rock falls, absorption of flushing fluid, "guttering") prevent the transfer of the required load. Difficulty in reloading may be due to improper placement of the hydraulic jar in the drill string.

- As a result of intensive jar work, the working fluid was heated, with which the hydraulic jar was filled. As the temperature of the working fluid rises, its viscosity decreases, as a result of which the hydraulic part of the jar may fail, and there will be no hydraulic delay.

The mechanical part of the jar will remain functional, while the impact force will correspond to the release force, but it will be impossible to adjust the impact force. In order to restore the efficiency of the jar, it is necessary to suspend its operation to cool the working fluid for approximately 30 minutes.

The technical result of the double-acting hydraulic jar presented in this description is to increase its resource and reliability, the formation of ultra-high shock power in the wellbore with an optimal ratio between shock load and shock impulse, an increase in the accuracy of the delay time created by hydraulics, and a decrease in pressure losses during instantaneous pressure relief working fluid from the high-pressure chamber, and as part of the BHA - increasing the reliability of releasing the drill string from sticking in the well when drilling complex deviated wells with a high coefficient of friction, where it is difficult to create the axial force necessary for reloading the jar, mainly for working with the allowable tension force of the drill string and triggering the jar with repeated upstrokes.

The essence of the technical result presented in this description lies in the fact that in a double-acting hydraulic drilling jar, consisting of a tubular body and a hollow shaft, telescopically connected to each other, the tubular body is made of parts, contains a thread on the fluid inlet side, contains protrusions -anvils, on the fluid outlet side it contains slots on the inner surface and a sealant, the hollow shaft is made of parts, contains the first piston with a sealant on the fluid outlet side, impactors located between the anvil protrusions of the tubular body, on the fluid outlet side it contains the second a piston with a seal, forming a chamber filled with a working fluid - oil, a threaded shank and splines - on the outer surface, and also containing two limiting mechanisms for communicating the fluid with the fluid chamber, each of which is made in the form of a thickening of a hollow shaft, as well as the first and second ring valves, each which is installed in the working fluid chamber with a hollow shaft passing through the internal cavity, the inner surface of each annular valve is in close contact with the thickening of the hollow shaft, while each annular valve has a valve device that limits the flow of fluid inside the working fluid chamber in one direction, and the first the valve device of the first annular valve is located in such a way that it restricts the flow of fluid in the opposite direction relative to the fluid flow in the second valve device of the second annular valve, and also containing the valve body, inside which the valve seat, the spacer, as well as the first and second annular valves mentioned above valves, while the valve body is fastened to the parts of the tubular body, inside which the first piston with a seal and, accordingly, the second piston with a seal are installed, in each annular valve the above-mentioned valve device is installed, limiting its fluid flow inside the working fluid chamber in one direction, and the first valve device of the first annular valve is located in such a way that limits the fluid flow in the opposite direction relative to the fluid flow in the second valve device of the second annular valve, while the valve body is made with an internal annular belt, the spacer sleeve is installed with axial play between the first and second annular valves mentioned above, the valve seat is provided with a seal in contact with the inner surface of the valve body, according to the invention, the valve body is installed with the end of the inner annular belt directed towards the outlet of the fluid from the hollow shaft, the valve seat is placed between the end of the inner annular belt of the valve body and the first annular valve, in the first annular valve located on the side of the fluid medium inlet to the hollow shaft and placed in the working fluid chamber with a hollow shaft passing through the inside lower cavity of the working fluid chamber, a lower throttle device is installed that limits the flow of the working fluid in the same direction as the first valve device from the working fluid chamber formed by the second piston with a seal located on the side of the fluid outlet from the hollow shaft, the inner surface of the first annular valve, tightly in contact with the thickening of the hollow shaft and the tightly contacting end of the said annular valve with the end of the valve seat, and in the second annular valve located on the side of the fluid exit from the hollow shaft and placed in the working fluid chamber with a hollow shaft passing through the internal cavity of the working fluid chamber, an upper throttle device is installed that limits the flow of the working fluid in one direction with the second valve device from the working fluid chamber formed by the first piston with a seal located on the side of the fluid medium inlet to the hollow shaft, the inner surface of the second about the annular valve, tightly contacting with the thickening of the hollow shaft and tightly contacting the end of the said annular valve with the end of the tubular body directed towards it, while the time T of the hydraulic delay of the hydraulic drilling jar, the time T _d of the hydraulic delay of the first valve device located in the first annular valve , and the time T _{p of} the hydraulic delay of the lower throttle device located in the first annular valve, are related by the relationship: T=(0.25÷0.75) (T _d +T _p ), and the time N of the hydraulic delay of the hydraulic drilling jar, time N _d hydraulic delay of the second valve device, located in the second ring valve, and the time N _p of the hydraulic delay of the upper throttle device, located in the second ring valve, are related by the ratio: N=(0.25÷0.75) (N _d +N _p ) .

The volume of the compartment V _p of the fluid chamber with a hollow shaft passing through the inner cavity of the working fluid chamber, formed by a second piston with a seal located on the side of the fluid outlet from the hollow shaft, the inner surface of the second annular valve, tightly in contact with the thickening of the hollow shaft and tightly contacting the end face of said annular valve with the end face of a part of the tubular body, and the volume of the compartment V _d of the working fluid chamber with a hollow shaft passing through the inner cavity of the working fluid chamber formed by the first piston with a seal located on the side of the fluid inlet into the hollow shaft, the inner surface of the second annular valve, tightly contacting with the thickening of the hollow shaft and tightly contacting the end of the said annular valve with the end face of the part of the tubular body when the body is stretched relative to the hollow shaft, at the moment the inner surface of the second annular valve is torn off from the belt of the increased diameter of the hollow shaft, are connected ratio: V _p =(0.85÷l.15) V _d Ф, where Ф=1.618 is a constant coefficient.

The tubular body on the side of the fluid medium inlet is equipped with a sub made with a belt of reduced rigidity, characterized by the execution of the wall of the sub with a reduced thickness and a reduced outer diameter, forming a thrust end with the possibility of capturing and holding the drill pipe string during descent and retrieval from the well.

A certain impact force is required to instantly release a stuck drill string. When the impact force exceeds the sticking force, the impact momentum causes the drill pipe sticking point to slip. Striking force is the main factor. In the best ratio, a certain dynamic impact with a sufficient impact impulse, in essence, with an ultra-high impact power, is needed.

Execution of a double-acting hydraulic drilling jar in such a way that the valve body is installed with the direction of the end of the inner annular belt towards the outlet of the fluid from the hollow shaft, the valve seat is placed between the end of the inner annular belt of the valve body and the first annular valve, in the first annular valve located with side of the fluid medium inlet to the hollow shaft and placed in the working fluid chamber with a hollow shaft passing through the internal cavity of the working fluid chamber, a lower throttle device is installed that limits the flow of the working fluid in one direction with the first valve device from the working fluid chamber formed by the second piston with a seal located on the side of the exit of the fluid from the hollow shaft, the inner surface of the first annular valve in close contact with the thickening of the hollow shaft and the tightly contacting end of the said annular valve with the end face of the valve seat, and in the second rings The second valve, located on the side of the fluid exit from the hollow shaft and located in the working fluid chamber with a hollow shaft passing through the internal cavity of the working fluid chamber, has an upper throttle device that limits the flow of the working fluid in the same direction as the second valve device from the working fluid chamber formed by the first piston with a seal located on the side of the fluid medium inlet to the hollow shaft, the inner surface of the second annular valve in close contact with the thickening of the hollow shaft and the tightly contacting end of the said annular valve with the end of the part of the tubular body directed towards it, while the time T of the hydraulic the delay of the hydraulic drilling jar, the time T _d of the hydraulic delay of the first valve device located in the first annular valve, and the time T _{p of} the hydraulic delay of the lower throttle device located in the first annular valve, are related by the ratio: T=(0.25÷0.75) (T _d +T _p ), and the hydraulic delay time N of the hydraulic drilling jar, the hydraulic delay time N _d of the second valve device located in the second annular valve, and the hydraulic delay time N _p of the upper throttle device located in the second annular valve are related by the relation : N=(0.25÷0.75) (N _d +N _P ), provides an increase in its resource and reliability, the formation of ultra-high shock power in the wellbore with an optimal ratio between shock load and shock impulse, increasing the accuracy of the delay time created hydraulics, and as part of the BHA - increasing the reliability of releasing the drill string from sticking in the well when drilling complex deviated wells with a high coefficient of friction, where it is difficult to create the axial force necessary for recharging the jar, mainly for working with an allowable tension force of the drill string and triggering the jar by repeated blows up.

Such a design of a double-acting hydraulic drilling jar simplifies the design, reduces the cost of manufacture, maintenance and repair, increases the reliability (reduces "sensitivity" to oil contamination) of the valve and throttle devices of the first and second annular valves during repeated dynamic shock and instantaneous pressure relief of the working fluid from the chamber (sections) of high pressure through the slotted channels formed by the inner surfaces of the first and, respectively, the second annular valves and the outer surface of the corbel of the increased diameter of the hollow shaft, improves the hydrodynamic centering of the hollow shaft in the tubular body, prevents distortions and sticking in the friction surfaces due to cyclic bending stresses tubular body during rotation of a curved drill string (during rotary drilling).

Execution of a double-acting hydraulic drilling jar in such a way that the volume of the compartment V _p of the fluid chamber with a hollow shaft passing through the internal cavity of the working fluid chamber, formed by a second piston with a seal located on the side of the fluid outlet from the hollow shaft, the inner surface of the second annular valve , in close contact with the thickening of the hollow shaft and in close contact with the end of the said annular valve with the end of the part of the tubular body, and the volume of the compartment V _d of the working fluid chamber with a hollow shaft passing through the inner cavity of the working fluid chamber, formed by the first piston with a seal located on the inlet side fluid medium into the hollow shaft, the inner surface of the second annular valve in close contact with the thickening of the hollow shaft and the tightly contacting end of the said annular valve with the end of the part of the tubular body when the body is stretched relative to the hollow shaft, at the moment of failure of the internal surface The values of the second annular valve from the girdle of the increased diameter of the hollow shaft are related by the ratio: V _p = (0.85÷4.15) V _d F, where F=1.618 is a constant coefficient (Fibonacci number), provides the formation of ultra-high impact power in the wellbore with an optimal (best) ratio between shock load and shock impulse acting upwards (for example, 600 blows continuously upwards) at the place of sticking of the drill string, prevents uncontrolled activation and spontaneous strikes as a result of reaction to the longitudinal force applied to the drill string and jar and also prevents scuffing and sticking in the sliding surfaces of the mandrel in the body, caused by cyclic bending stresses of the body during rotation of the bent drill string in the well (during rotary drilling).

Increasing the accuracy of the jar response delay time created by hydraulics, essentially the throttling time of a limited volume of working fluid in the first annular valve located on the side of the fluid medium inlet to the hollow shaft and placed in the working fluid chamber with a hollow shaft passing through the internal cavity of the working fluid chamber , in which a lower throttle device is installed that limits the flow of the working fluid in one direction with the first valve device from the working fluid chamber formed by the second piston with a seal located on the side of the fluid outlet from the hollow shaft, the inner surface of the first annular valve in close contact with the thickening of the hollow shaft and the tightly contacting end of said annular valve with the end of the valve seat, as well as in the second annular valve located on the side of the fluid exit from the hollow shaft and placed in the working fluid chamber with a hollow shaft passing through the internal the upper cavity of the working fluid chamber, in which the upper throttle device is installed, which limits the flow of the working fluid in one direction with the second valve device from the working fluid chamber formed by the first piston with a seal located on the side of the fluid medium inlet to the hollow shaft, the inner surface of the second annular valve , tightly contacting with the thickening of the hollow shaft and tightly contacting the end of the said annular valve with the end of the part of the tubular body directed towards it, for striking at the optimal ratio between the shock load and the shock impulse, allows the operator at the drilling rig to set the calculated tension force of the drill string, and then apply drawworks brake.

As a result, the sticking release force is controlled with a predetermined accuracy, damage to the bottom hole bit and threaded joints of the bottomhole assembly (BHA) is prevented, it is possible to release the drill string from sticking in a complex deviated well with a high friction coefficient, where it is difficult to create the necessary for jar reloading axial force, mainly for working with allowable (metered) pulling force of the drill string and triggering the jar with repeated upward blows, for example, in a BHA with a gyrotorque hydraulic motor for rotary drilling (with rotation of the drill string) of a directional well and a horizontal interval of the well.

Execution of the hydraulic drilling jar in such a way that the tubular body on the side of the fluid medium inlet is equipped with a sub made with a belt of reduced rigidity, characterized by the execution of the wall of the sub with reduced thickness and a reduced outer diameter, forming a thrust end with the possibility of capturing and holding the drill string during descent and retrieval from the well, provides reliable retention of the drill pipe string and prevents damage to the tubular body by clamps (sliders) or rig elevator cams. Below is a double-acting hydraulic drilling jar RJ-2H-9.5.800 RS for releasing a drill string from sticking in a directional well, drilling interval: 3500-4500 m.

In FIG. 1 shows a double-acting hydraulic drilling jar (in longitudinal section): a sub for connecting to a drill string, a part of the tubular body on the fluid inlet side, a valve body, the middle and lower parts of the tubular body, a hollow shaft installed inside the tubular body and the valve body .

In FIG. 2 shows element I in FIG. 1: valve body, valve seat, spacer, first and second ring valves, hollow shaft through fluid chamber.

In FIG. 3 shows element I in FIG. 1: valve body, valve seat, spacer, first and second annular valves, hollow shaft passing through the fluid chamber (when the drill string is lowered into the well) at the moment the inner surface of the first annular valve is torn off from the thickening of the hollow shaft.

In FIG. 4 shows element I in FIG. 1: valve body, valve seat, spacer, first and second annular valves, hollow shaft passing through the fluid chamber (when the drill string is under tension) at the moment the inner surface of the second annular valve is torn off the hollow shaft thickening.

In FIG. 5 shows element II in FIG. 1 of a tubular body and a first piston with a first seal attached to the top of the hollow shaft.

In FIG. 6 shows element III in FIG. 1 of the tubular body and the second piston with the second seal, made in one piece with the hollow shaft, a shock ring is placed between the ends of the splines of the hollow shaft and the striker.

In FIG. 7 shows element IV in FIG. 1 seal at the bottom of the tubular housing for the hollow shaft.

The double-acting hydraulic drilling jar consists of a tubular body 1 and a hollow shaft 2, telescopically connected to each other, the tubular body 1 is made of parts 3, 4, 5, contains a thread 6 from the side of the first edge 7, in the middle part 5 of the tubular body 1 contains an internal protrusion-anvil 8, and from the side of the second edge 9 contains slots 10 on the inner surface of part 5 of the tubular body 1, and also contains a seal 11 of part 5 of the tubular body 1, while pos.12 is a sub for connection with the lower part of the upper string of drill pipes (not shown) is shown in Fig. 1, 6, 7.

The hollow shaft 2 is made of parts 13 and 14, contains from the side of the first edge 7 of the tubular body 1 the first piston 15 with the first seal 16, the striker 17, placed on the part 13 of the hollow shaft 2, directed to the inner protrusion-anvil 8 of the middle part 5 of the tubular body 1, and the striker 18, essentially, the end 18 of the part 14 of the hollow shaft 2, directed to the second edge 9, essentially, to the end 9 of the part 5 of the tubular body 1, while the end 19 of the part 13 of the hollow shaft 2 does not interact with the inner conical surface 20 of the part 4 of the tubular body 1 is shown in FIG. 1, 2, 3, 4, 6, 7.

From the second edge 9 of the tubular body 1, the hydraulic drilling jar contains a second piston 21, made in one piece with part 13 of the hollow shaft 2, the second piston 21 is made with a second seal 22, forming a chamber 23 filled with a working fluid-oil 24, for example, gear oil SAE 80W-140 (SAE J 306, USA and Western Europe), part 14 of the hollow shaft 2 includes a threaded shank 25 and splines 26 on the outer surface of the part 14 of the hollow shaft 2, while the outer surface of the part 14 of the hollow shaft 2 is made with a coating of hard alloy, shown in Fig. 1, 6, 7.

The double-acting hydraulic drilling jar contains two limiting mechanisms 27 and 28 for communication of the working fluid-oil 24 with the fluid chamber 23 24, shown in FIG. 1, 2, 3, 4, 5, 6.

The limiting mechanism 27 for communicating fluid 24 with chamber 23 for fluid 24 is made in the form of a thickening 29 of part 13 of hollow shaft 2, as well as the first annular valve 30 (made of bronze BrA10Zh4N4L GOST 493-79), which is installed in chamber 23 of working fluid 24 with part 13 of the hollow shaft 2 passing through the chamber 23 of the working fluid 24, the inner surface 31 of the first annular valve 30 is in close contact with the thickening 29 of the part 13 of the hollow shaft 2, while the first annular valve 30 has the first valve device 32, which limits the flow of the working fluid-oil 24 in one direction, essentially in the direction of arrow 33, shown in FIG. 1, 2, 3.

In the first annular valve 30 upstream 33 in front of the first valve device 32 there is a filter 34 made of "sintered" bronze powder (made of bronze BrA10Zh4N4L GOST 493-79), porosity 25-50%, hollow screw 35 with an internal hexagon for circulation of the working fluid 24 in the valve arrangement 32 shown in FIG. 1, 2, 3.

The limiting mechanism 28 for communicating the fluid 24 with the chamber 23 for the fluid 24 is located in the opposite direction (opposite) relative to the restricting mechanism 27 for communicating the working fluid 24 with the chamber 23 for the fluid 24, essentially in the form of the same thickening 29 of the part 13 of the hollow shaft 2, and also the second annular valve 36 (made of bronze BrA10Zh4N4L GOST 493-79), which is installed in the chamber 23 of the working fluid 24 with part 13 of the hollow shaft 2 passing through the internal cavity, essentially through the chamber 23 of the working fluid 24, while the inner surface 37 the second annular valve 36 is in close contact with the thickening 29 of the part 13 of the hollow shaft 2, while in the second annular valve 36 is installed in the opposite direction, opposite the valve device 32, the second valve device 38, which limits the flow of the working fluid-oil 24 in the direction of the arrow 39, is shown in fig. 1, 2, 3, 4.

In the second annular valve 36 upstream 39 in front of the second valve device 38, there is also a filter 34 made of "sintered" bronze powder (from bronze BrA10Zh4N4L GOST 493-79), porosity 25-50%, hollow screw 35 with an internal hexagon for circulation of the working fluid 24 in valve assembly 38 is shown in FIG. 1, 2, 3, 4.

The working fluid 24 can flow (during the reverse stroke) through the circulation holes 40 of the annular valve 30, as well as through the circulation holes 41 of the annular valve 36, to quickly equalize the pressure of the fluid 24 from different sides of the annular valve 30 and, accordingly, the annular valve 36, shown in Fig. . 1, 3, 4.

The first valve device 32, located in the first annular valve 30, limits the flow rate (throttles) the flow of the working fluid 24 along the arrow 33 in the opposite direction relative to the flow of fluid 24 along the arrow 39 in the second valve device 38, located in the second annular valve 36, is shown in fig. 1, 2, 3, 4.

Double-acting hydraulic drilling jar contains a valve body 42, inside of which there is a valve seat 43, a spacer 44, as well as the first and second annular valves mentioned above, respectively, 30 and 36, while the valve body 42 is threaded 45 with part 3 of the tubular body 1, and is also threaded 46 with part 4 of the tubular body 1, inside which the first piston 15 with the first seal 16 and, accordingly, the second piston 21 with the second seal 22 are installed, in each annular valve 30, 36 the above-mentioned valve device 32 is installed, 34, 35 and, respectively, 38, 34, 35, restricting the flow of fluid 24 inside the chamber 23 of the working fluid 24 in one direction 33 or 38, is shown in FIG. 1, 2, 3, 4.

The valve body 42 is made with an internal annular belt 47, the spacer 44 is installed with an axial play 48 (for example, 5 mm), between the first annular valve 30 and the second annular valve 36, the valve seat 43 is provided with a seal 49 in contact with the inner surface 50 of the body 42 valves shown in Fig. 1, 2, 3, 4.

The valve body 42 is mounted with the end 51 of the inner annular belt 47 directed towards the outlet 52 of the fluid 53 from the hollow shaft 2, and the valve seat 43 is placed between the end face 51 of the inner annular belt 47 of the valve body 42 and the first annular valve 30, shown in FIG. 1, 2, 3, 4.

In the first annular valve 30 installed in the chamber 23 of the working fluid 24 with a hollow shaft 2 passing through the internal cavity of the chamber 23 of the working fluid 24, located on the side of the inlet 54 of the fluid 53 into the hollow shaft 2, a lower throttle device 55 (manufactured in Russia) is installed limiting the flow of the working fluid 24 in the same direction 33 with the first valve device 32, 34, 35 from the compartment 56 of the chamber 23 of the working fluid 24, formed by the second piston 21 with a seal 22, located on the side of the exit 52 of the fluid 53 from the hollow shaft 2, the inner the surface 31 of the first annular valve 30 in close contact with the thickening 29 of the part 13 of the hollow shaft 2 and the end face 57 of said annular valve 30 in close contact with the end face 58 of the valve seat 43 is shown in FIG. 1, 3, 6.

In the second annular valve 36 installed in the chamber 23 of the working fluid 24 with a hollow shaft 2 passing through the internal cavity of the chamber 23 of the working fluid 24, located on the side of the outlet 52 of the fluid 53 from the hollow shaft 2, there is an upper throttle device 59 (manufactured in Russia) limiting the flow of the working fluid 24 in one direction 39 with the second valve device 38, 34, 35 from the compartment 60 of the chamber 23 of the working fluid 24, formed by the first piston 15 with a seal 16, located on the side of the inlet 54 of the fluid 53 into the hollow shaft 2, the inner the surface 37 of the second annular valve 36, which is in close contact with the thickening 29 of the part 13 of the hollow shaft 2 and the tightly contacting end 61 of the said annular valve 36 with the end 62 of the part 4 of the tubular body 1 directed towards it, is shown in FIG. 1, 4, 5.

Part 3 of the tubular body 1, designed for telescopic movement of the first piston 15 with the first seal 16, forming with part 13 of the hollow shaft 2 a chamber 23 filled with working fluid - oil 24, has a coating in the form of chromium and an inner diameter 63, D, is shown in Fig. . fifteen.

Part 4 of the tubular body 1, designed for telescopic movement of the second piston 21 with the second seal 22, forming with part 13 of the hollow shaft 2 chamber 23 filled with working fluid - oil 24, also has a coating in the form of chromium and the same inner diameter 63, D, shown in fig. 16.

The lifting device on the drilling rig creates a tensile force on the drill string and "throws" it down, giving the drill string a downward impact impulse.

The hydraulic delay time T of the hydraulic jar, essentially for applying dynamic impacts with the jar in the downward direction, the hydraulic delay time T _d of the first valve device 32, 34, 35 located in the first annular valve 30, and the hydraulic delay time Tr of the lower throttle device 55 , located in the first annular valve 30, are related by the ratio: T=(0.25÷0.75) (T _d +T _p ), shown in Fig. 1, 2, 3.

To strike upwards, a load of the calculated value is applied, and then the drawworks brake is applied using a computer.

The hydraulic delay time N of the hydraulic jar, essentially for applying dynamic blows with the jar in the upward direction, the hydraulic delay time N _d of the second valve device 38, 34, 35 located in the second annular valve 36, and the hydraulic delay time N _p of the upper throttle device 59, located in the second annular valve 36, are related by the ratio: N=(0.25÷0.75) (N _d +N _P ), shown in FIG. 1, 2, 4.

Between the ends 64 of the splines 26 on the outer surface of the part 14 of the hollow shaft 2 and the striker 17 of the part 13 of the hollow shaft 2 directed towards the splines 26, a shock ring 65 is placed, where pos.66 is the end face of the shock ring 65, shown in Fig. 6.

In addition, pos.67 - slotted chamber located between the seal 11 of part 5 of the tubular body 1 and the second seal 22 of the piston 21, made in one piece with part 13 of the hollow shaft 2, also filled with working fluid 24 - gear oil SAE 80W-140, shown in Fig. 16.

In addition, pos.68 - threaded plugs in places with the largest wall thickness of the housing 1 for supplying the working fluid 24 - transmission oil SAE 80W-140 into the chamber 23, as well as into the slotted chamber 67, is shown in Fig. 1, 2, 3, 4.7.

The volume 56, V _p of the chamber 23 of the working fluid 24, is essentially the volume of the compartment 56 of the chamber 23 of the working fluid 24 with a hollow shaft 2 passing through the internal cavity of the chamber 23 of the working fluid 24, formed by the second piston 21 with a seal 22 located on the output side 52 fluid medium 53 from the hollow shaft 2, the inner surface 37 of the second annular valve 36, in close contact with the thickening 29 of the part 13 of the hollow shaft 2 and the tightly contacting end 61 of the said annular valve 36 with the end face 62 of the part 4 of the tubular body 1 when the tubular body 1 is stretched relative to the hollow shaft 2 (when the drill string is tensioned), at the moment of failure of the inner surface 37 of the second annular valve 36 from the thickening 29 of the part 13 of the hollow shaft 2, and the volume of the compartment 60, V _d of the chamber 23 of the working fluid 24 with a hollow shaft 2 passing through the inner cavity of the chamber 23 of the working fluid 24 formed by the first piston 15 with a seal 16 located on the side of the inlet 54 of the fluid 53 into the hollow shaft 2, the inner surface 37 of the second annular valve 36, which is in close contact with the thickening 29 of the part 13 of the hollow shaft 2 and the tightly contacting end face 61 of the said annular valve 36 with the end face 62 of the end face of the part 4 of the tubular body 1, are connected by the ratio: V _p =(0.85÷1, 15) V _d Ф, where Ф=1.618 is a constant coefficient (Fibonacci number), shown in FIG. fourteen.

The tubular body 1 from the side of the inlet 7 of the fluid 53 is equipped with a sub 12, designed to be connected by thread 70 with the bottom of the upper part of the drill string (not shown), made with a belt 71 of reduced rigidity, characterized by the execution of the wall of the sub 12 with a reduced thickness 72 and a reduced outer diameter 73, forming a thrust end 74 with the ability to capture and hold the drill string during the descent and retrieval from the well, is shown in FIG. one.

Below are the parameters of the double-acting hydraulic drilling jar RJ-2H-9.5.800 RS, which are given in tables 1, 2.

The chambers 23 for the working fluid 24 are filled through the threaded holes for the plugs 68 with the working fluid 24 (gear oil SAE 80W-140), the working fluid 24 is pumped to remove air, then the plugs 68 are tightened.

Tests of the double-acting hydraulic drilling jar RJ-2H-9.5.800 RS are carried out in the stand, patent RU 2491528 C2 of Radius-Service (RU), which is part of Schlumberger (US)

Double-acting hydraulic drilling jar RJ-2H-9.5.800 RS is sent to the drilling rig.

The best position of the jar in the bottom hole assembly is determined, taking into account technological factors, for example, the expected type of sticking (due to differential pressure or mechanical), the trajectory and angle of inclination of the wellbore, the configuration of the bottom hole assembly, the pump pressure, the coefficient of buoyancy of the drilling fluid, the value limit load on the bit, allowable pulling force of the drill string, tensile strength of the drill pipe.

The hydraulic drilling jar is connected by thread 6 of part 3 of the tubular body 1 to sub 12, the sub 12 is connected to the bottom of the upper part of the drill string used in drilling an oil well, and the threaded shank 25 of part 14 of the hollow shaft 2 is connected to the top of the lower part of the drill string.

A drilling pump, for example, UNB-600, pumps a fluid medium through a drill pipe string, for example, polymer-clay drilling mud 17, density 2.2 g/cm ³ , viscosity 90 s, containing solid phases of the solution - sand with dimensions 0 , 15 ÷ 0.95 mm, sand content is not more than 1%, and up to 5% of oil products, while the hydrostatic pressure of the drilling fluid inside the hollow shaft 2 and the tubular body 1, supplied from the wellhead to the bit in direction 53, during rotary drilling ( with the rotation of the drill string) by a gerotor hydraulic motor is 35÷45 MPa.

The drilling of the well is carried out by rotating the drill string by the rotor of the drilling rig 5000EU with a rotation speed of 20÷30 rpm during operation of the gerotor hydraulic motor rotating the bit, while the flow of drilling mud 53 ensures flushing of the bottom of the well and removal of the drilled rock to the surface.

A hydraulic drilling jar is operated by upward and/or downward movement of the drill string in response to longitudinal force applied to the drill string and jar.

The magnitude of the upward impact force is directly proportional to the applied tensile force.

The movement of the jar at the initial stage is restrained by a hydraulic pair: the limiting mechanism 28 for communicating the fluid 24 with the chamber 23 for the fluid 24, made in the form of a belt 29 of increased diameter of the part 13 of the hollow shaft 2, the second annular valve 36, which is installed in the chamber 23 of the working fluid 24 with the part 13 of the hollow shaft 2 passing through the chamber 23 of the working fluid 24, the inner surface 37 of the second annular valve 36 is in close contact with the thickening 29 of the part 13 of the hollow shaft 2, the second valve device 38, which limits the flow of the working fluid-oil 24 in one direction, essentially, in the direction of the arrow 39, as well as the upper throttle device 59, which limits the flow of the working fluid 24 in the same direction 39 with the second valve device 38 from the compartment 60 of the chamber 23 of the working fluid 24, formed by the first piston 15 with a seal 16, located on the side of the inlet 7 of the fluid medium 53 into the hollow shaft 2, the inner surface 37 of the second annular valve and 36, tightly contacting with the thickening 29 of the part 13 of the hollow shaft 2 and the tightly contacting end face 61 of the annular valve 36 with the end face 62 of the part 4 of the tubular body 1, and is maintained until the required tensile stresses (permissible forces) are created in the drill string drill string tension).

The stage of free movement of parts inside the jar is designed to relax stresses, in essence, to abruptly remove part of the tensile stresses accumulated in the tensioned drill string, shown in Fig. 1, 3, 6.

Such drill string stress relief is used to accelerate the drill collars and/or the entire mass of the drill string and create a shock pulse downhole within the shock section of the hydraulic drill jar.

Typically, drill collars (DCs) are used to concentrate a large mass directly above the jars, essentially where the maximum speed is reached when the jar is released or free-floating is completed.

A stress wave in the drill string occurs as a result of a sudden stop of the moving mass of couplings and drill collars, while the kinetic energy is converted into the energy of the stressed state.

The stress wave simultaneously moves up to the sleeves and drill collars and down to the sticking point. A stress wave that is transmitted upward to the couplings or heavy weight will move upward until it reaches a sectional change, such as transition from coupling to heavy weight and collar. Then it will be reflected down.

The stress wave that originally traveled down from the jar reaches the sticking point and is reflected back up. After some time, the combination of stress waves at the sticking point determines the magnitude of the maximum applied load. In general, the greater the shock pulse applied to the tack, the lower the shock load. In this case, the stronger the dynamic impact, the smaller the impact impulse. Impact and momentum are needed.

A certain amount of impact force is required to release the clamp in an instant. When the impact force exceeds the tack force, the impact momentum causes the tack to slip. Striking force is the main factor. In the best ratio, a certain dynamic impact with a sufficient impact impulse, in essence, with an ultra-high impact power, is needed.

The optimal location of the hydromechanical jar is above the transition zone, however, the jar is also lowered below the transition zone.

The hydraulic drilling jar is lowered into the well with such a number of drill collars that provides the necessary weight on the bit and ensures that the jar is located above the transition zone.

Weight on bit is adjusted by adding or removing drill collars under the hydraulic jar while maintaining sufficient weight above the jar to provide effective jar strike.

When the stick is released, the drilling fluid circulates in the well, the pressure drop across the bit creates a force that stretches the jar, while taking into account the force of starting the pump, as this reduces the force required to strike the jar up and increases the force required to strike in the downward direction.

To compensate for friction losses on the wellbore walls of a curved drill string in a directional well, an additional tension force of the drill string is created, the amount of compensation is taken into account by the indications of the load on bit indicator during trips and rises until the drill string sticks, while the weight of the free string is the weight part of the column located above the jar.

Throwing dynamic blows with the jar in the upward direction:

To strike upwards, a load of the calculated value is applied, and then the drawworks brake is applied using a computer. The tubular body 1, connected to the adapter 12 and the upper part of the drill string, when the upper part of the drill string is tensioned, is pulled out of the hollow shaft 2, which is connected to the lower part of the drill string stuck in the inclined and (or) horizontal section of the oil well.

The piston 15 with the seal 16 creates an ultra-high pressure, essentially 125 MPa, in compartment 60 of the chamber 23 of the working fluid 24, filled with gear oil SAE 80W-140, with a hollow shaft 2 passing through the internal cavity of the chamber 23 of the working fluid 24 formed by the first piston 15 with a seal 16 located on the side of the inlet 7 of the fluid 53 into the hollow shaft 2, the inner surface 37 of the annular valve 36, in close contact with the thickening 29 of the part 13 of the hollow shaft 2 and the tightly contacting end 61 of the annular valve 36 with the end face 62 of the part 4 of the tubular body 1 when the tubular body 1 is pulled out of the hollow shaft 2 (when the drill string is pulled), shown in Fig. 1, 2, 4.

The end 57 of the annular valve 30 is not pressed by the pressure of the working fluid 24 to the end face 58 of the valve seat 43, the working fluid 24 can freely flow through the circulation holes 40 of the annular valve 30 to quickly equalize the pressure of the working fluid 24 from different sides of the annular valve 30, and the working fluid 24 in the time of pulling the tubular body 1 out of the hollow shaft 2 when the upper part of the drill string is tensioned cannot flow through the circulation holes 41 of the annular valve 36, is shown in FIG. 1, 2, 4.

In the annular valve 36 installed in the chamber 23 of the working fluid 24 with a hollow shaft 2 passing through the internal cavity of the chamber 23 of the working fluid 24, located on the side of the outlet 52 of the fluid 53 from the hollow shaft 2, the upper throttle device 59 limits the flow of the working fluid 24 in one direction 39 with the second valve device 38, 34, 35 from the compartment 60 of the chamber 23 of the working fluid 24, formed by the first piston 15 with the seal 16, located on the side of the inlet 54 of the fluid 53 into the hollow shaft 2, the inner surface 37 of the second annular valve 36, in close contact with the thickening 29 of the part 13 of the hollow shaft 2 and the tightly contacting end 61 of the said annular valve 36 with the end 62 of the part 4 of the tubular body 1 directed towards it, is shown in FIG. 1, 4, 5.

When the edge of the thickening 29 of the part 13 of the hollow shaft 2 is torn off from the edge of the inner surface 37 of the annular valve 36, a hydraulic impact of the working fluid 24 occurs in the cavity of the compartment 56, V _p of the chamber 23 of the working fluid 24 with a hollow shaft 2 passing through the inner cavity of the chamber 23 of the working fluid 24 , formed by the second piston 21 with a seal 22, located on the side of the exit 52 of the fluid 53 from the hollow shaft 2, the inner surface 37 of the annular valve 36, in close contact with the thickening 29 of the part 13 of the hollow shaft 2 and the tightly contacting end 62 of the part 4 of the tubular body 1, using the effect of "sudden expansion", with minimal pressure losses and the formation of ultra-high shock power in the wellbore with an optimal ratio between the shock load and the shock impulse acting on the place of the sticking of the string, while the striker 18 is essentially the end 18 of the hollow shaft part 14 2, strikes towards the second edge 9, essentially towards the butt 9 of part 5 tr gear housing 1, shown in Fig. fourteen.

The volume 56, V _p of the chamber 23 of the working fluid 24, is essentially the volume of the compartment 56 of the chamber 23 of the working fluid 24 with a hollow shaft 2 passing through the internal cavity of the chamber 23 of the working fluid 24, formed by the second piston 21 with a seal 22 located on the output side 52 fluid medium 53 from the hollow shaft 2, the inner surface 37 of the second annular valve 36, in close contact with the thickening 29 of the part 13 of the hollow shaft 2 and the tightly contacting end 61 of the said annular valve 36 with the end face 62 of the part 4 of the tubular body 1 when the tubular body 1 is stretched relative to the hollow shaft 2 (when the drill string is tensioned) at the moment of failure of the inner surface 37 of the second annular valve 36 from the thickening 29 of the part 13 of the hollow shaft 2, and the volume of the compartment 60, V _d of the chamber 23 of the working fluid 24 with a hollow shaft 2 passing through the internal cavity of the chamber 23 working fluid 24 formed by the first piston 15 with a seal 16 located on the side of the inlet 54 of the fluid 53 into the hollow shaft 2, in the inner surface 37 of the second annular valve 36, which is in close contact with the belt 29 of the increased diameter of the part 13 of the hollow shaft 2 and the tightly contacting end 61 of the said annular valve 36 with the end face 62 of the end face of the part 4 of the tubular body 1, are connected by the ratio: V _p =(0.85÷ 1.15) V _d Ф, where Ф=1.618 is a constant coefficient (Fibonacci number), shown in Fig. fourteen.

The hydraulic delay time N of the hydraulic jar, essentially for applying dynamic blows with the jar in the upward direction, the hydraulic delay time N _d of the second valve device 38, 34, 35 located in the second annular valve 36, and the hydraulic delay time N _p of the upper throttle device 59, located in the second annular valve 36, are related by the ratio: N=(0.25÷0.75) (N _d +N _P ), shown in FIG. 1, 2, 4.

As a result, accurate hydraulic "lag" time is provided to strike at the optimal ratio between shock load and shock impulse, and this allows the operator at the rig to change the allowable pulling force of the drill string, and then apply the drawworks brake, the sticking release force is precisely is controlled, full possibility of release from sticking of the drill string in the well is provided.

A stretched drill string loses elastic tensile stresses for, for example, 45 ms, and an effect of relaxation of elastic tensile stresses occurs in drill pipes and drill pipe joints.

The stress wave simultaneously moves up to the sleeves and drill collars and down to the sticking point. The stress wave that is transmitted upwards to the couplings or heavy weight travels upward until it reaches a sectional change, such as the transition from coupling to heavy weight and collar, then it is reflected downward.

The stress wave that originally traveled down from the jar reaches the sticking point and is reflected back up. After some time, the combination of stress waves at the sticking point determines the magnitude of the maximum applied load.

After striking upwards, the drill string is lowered until the load indicator shows a value less than the weight of the free string.

The jar is ready for the next hammering cycle by responding to the longitudinal force applied to the drill string and jar, or drilling can be resumed.

Delivering dynamic jarring strikes in a downward direction:

The lifting device on the drilling rig creates a tensile force on the drill string and "throws" it down, giving the drill string a downward impact impulse.

The tubular body 1, connected to the adapter 12 and the upper part of the drill string, when moving down the upper part of the drill string is pressed into the hollow shaft 2, which is connected to the lower part of the drill string stuck in the inclined and (or) horizontal section of the oil well.

Piston 21 with seal 22, forming a chamber 23 filled with working fluid 24, gear oil SAE 80W-140, creates an ultra-high pressure, essentially 125 MPa, in the chamber 23 of working fluid 24, located before the first annular valve 30, essentially between the annular valve 30 and a piston 21 with a seal 22, while the end 57 of the annular valve 30 is tightly pressed under the action of the pressure of the working fluid 24 to the end 58 of the valve seat 43, is shown in FIG. 1, 2, 3, 6.

In this case, the end 61 of the second annular valve 36 is not pressed by the pressure of the working fluid 24 to the end 52 of part 4 of the tubular body 1, the working fluid 24 can freely flow through the circulation holes 41 of the second annular valve 36 to quickly equalize the pressure of the working fluid 24 from different sides of the annular valve 36 , and the working fluid 24 during the movement of the tubular hollow body 1 when moving down the upper part of the drill string and pressing into the hollow shaft 2, which is connected to the lower part of the drill string stuck in the inclined and (or) horizontal section of the oil well, cannot flow through the circulation holes 40 of the first annular valve 30.

When the edge of the thickening 29 of the part 13 of the hollow shaft 2 is torn off from the edge of the inner surface 31 of the annular valve 30, hydraulic impact of the working fluid 24 occurs in the cavity between the annular valve 30 and the first valve 15 of the part 13 of the hollow shaft 2 with seals 16, using the effect of "sudden expansion" , with minimal pressure loss and the formation of ultra-high shock power in the wellbore with an optimal ratio between shock load and shock impulse acting on the stuck string.

In this case, the striker 17, placed on part 13 of the hollow shaft 2, directed towards the inner protrusion-anvil 8 of the middle part 5 of the tubular body 1, as well as the impact ring 65, placed between the ends 64 of the splines 26 on the outer surface of the part 14 of the hollow shaft 2 and directed towards slots 26 by the striker 17 of the part 13 of the hollow shaft 2, strike the inner protrusion-anvil 8 of the middle part 5 of the tubular body 1 at a controlled ratio between the shock load and the shock impulse, acting downward on the place of sticking of the string and (or) on the bit.

The hydraulic delay time T of the hydraulic jar, essentially for applying dynamic impacts with the jar in the downward direction, the hydraulic delay time T _d of the first valve device 32, 34, 35 located in the first annular valve 30, and the hydraulic delay time T _p of the lower throttle device 55, located in the first annular valve 30, are related by the ratio: T=(0.25÷0.75) (T _d +T _p ), shown in FIG. 1, 2, 3.

The stress wave simultaneously moves down to the sticking point and up to the couplings and collars. The stress wave that is transmitted upwards to the couplings or heavy weight travels upward until it reaches a sectional change, such as the transition from coupling to heavy weight and collar, then it is reflected downward.

The stress wave that originally traveled down from the jar reaches the sticking point and is reflected back up. After some time, the combination of stress waves at the sticking point determines the magnitude of the maximum applied load.

In order for dynamic shock to occur again, the drill string is raised until the load indicator registers an increase in weight above the weight of the free string.

For the entire period of operation of the RJ-2H-110.800 double-acting hydraulic drilling jars, there have been no cases of damage or failure in operation, the resource of the hydraulic drilling jar is at least 600 hours when drilling complex deviated wells with a high coefficient of friction, where it is difficult to create the axial thrust necessary for reloading the jar. force, for example, in a deviated well with a mark of 4500 meters, having a horizontal interval of 1550 meters (well in DE, 2020) in this case, sticking in the well was eliminated, and the maximum time of the jar in the BHA was continuously 60 hours and during this time they were given 600 upstrokes and 45 downstrokes.

The resource and reliability of the most powerful double-acting hydraulic drilling jar in Russia is increased (maximum diameter 260 mm, the maximum allowable tensile (compressive) load transmitted to the jar parts during hydraulic delay is 140,000 kgf, the maximum allowable tensile load transmitted to the jar parts , - 800,000 kgf), provides ultra-high shock power in the wellbore with an optimal ratio between shock load and shock impulse, and as part of the BHA, it increases the reliability of releasing the drill string from sticking in the well when driving complex deviated wells with a high friction coefficient, where it is difficult to create the axial force required to reload the jar, mainly to work with the allowable pulling force of the drill string and trigger the jar with repeated upward blows.

Claims (3)

1. Double-acting hydraulic drilling jar, consisting of a tubular body and a hollow shaft, telescopically connected to each other, the tubular body is made of parts, contains a thread on the side of the fluid inlet, contains protrusions-anvils, on the side of the fluid outlet contains slots on the inner surface and a seal, the hollow shaft is made of parts, contains the first piston with a seal on the side of the fluid medium inlet, the impactors located between the protrusions-anvils of the tubular body, on the side of the fluid medium outlet contains the second piston with a seal, forming a chamber filled with a working fluid - oil, threaded shank and splines - on the outer surface, and also containing two limiting mechanisms for communicating fluid with a fluid chamber, each of which is made in the form of a hollow shaft thickening, as well as the first and second annular valves, each of which is installed in the working fluid chamber with a hollow shaft passing through the inner strips that is, the inner surface of each annular valve is in close contact with the thickening of the hollow shaft, while each annular valve has a valve device that limits the flow of fluid inside the working fluid chamber in one direction, and the first valve device of the first annular valve is located in such a way that limits the flow of liquid in the opposite direction with respect to the flow of fluid in the second valve device of the second annular valve, and also containing a valve body, inside which there is a valve seat, a spacer sleeve, as well as the first and second annular valves mentioned above, while the valve body is fastened to parts of the tubular body, inside which the first piston with a seal and, accordingly, the second piston with a seal are installed, while the valve body is made with an internal annular belt, the spacer sleeve is installed with axial play between the first and second annular valves mentioned above, the valve The valve seat is provided with a seal in contact with the inner surface of the valve body, characterized in that the valve body is installed with the direction of the end of the inner annular belt towards the outlet of the fluid from the hollow shaft, the valve seat is placed between the end face of the inner annular belt of the valve body and the first annular valve, in the first an annular valve located on the side of the fluid medium inlet to the hollow shaft and located in the working fluid chamber with a hollow shaft passing through the internal cavity of the working fluid chamber, a lower throttle device is installed that limits the flow of the working fluid in the same direction as the first valve device from the working fluid chamber formed by the second piston with a seal located on the side of the fluid exit from the hollow shaft, the inner surface of the first annular valve in close contact with the thickening of the hollow shaft and tightly contacting the end face of the said annular valve with the end face of the valve seat for, and in the second annular valve located on the side of the fluid outlet from the hollow shaft and placed in the working fluid chamber with a hollow shaft passing through the inner cavity of the working fluid chamber, an upper throttle device is installed that limits the flow of the working fluid in one direction with the second valve a device from a working fluid chamber formed by the first piston with a seal located on the side of the fluid medium inlet to the hollow shaft, the inner surface of the second annular valve in close contact with the thickening of the hollow shaft and the tightly contacting end of the said annular valve with the end of the part of the tubular body directed towards it, while the time T of the hydraulic delay of the hydraulic drilling jar, the time T _d of the hydraulic delay of the first valve device located in the first annular valve, and the time T _{p of} the hydraulic delay of the lower throttle device located in the first annular valve are connected ratio: T=(0.25÷2.75) (T _d +T _p ), and the time N of the hydraulic delay of the hydraulic drilling jar, the time N _d of the hydraulic delay of the second valve device located in the second annular valve, and the time N _p of the hydraulic the delays of the upper throttle device located in the second annular valve are related by the ratio: N=(0.25÷0.75) (N _d +N _p ). 2. Hydraulic drilling jar according to claim 1, characterized in that the volume of the compartment V _p of the fluid chamber with a hollow shaft passing through the internal cavity of the working fluid chamber, formed by a second piston with a seal located on the side of the fluid outlet from the hollow shaft, the inner the surface of the second annular valve in close contact with the thickening of the hollow shaft and the tightly contacting end of the said annular valve with the end face of the tubular body, and the volume of the compartment V _d of the working fluid chamber with a hollow shaft passing through the inner cavity of the working fluid chamber formed by the first piston with a seal, located on the side of the fluid medium inlet to the hollow shaft, the inner surface of the second annular valve in close contact with the thickening of the hollow shaft and the tightly contacting end of the said annular valve with the end of the part of the tubular body when the body is stretched relative to the hollow shaft, at the time of the breakdown of the inner surface of the second annular th valve from the thickening of the hollow shaft, are related by the ratio: V _p \u003d (0.85 ÷ 1.15) V _d Ф, where Ф \u003d 1.618 is a constant coefficient. 3. Hydraulic drilling jar according to claim 1, characterized in that the tubular body on the side of the fluid inlet is equipped with a sub made with a belt of reduced rigidity, characterized by the execution of the wall of the sub with reduced thickness and a reduced outer diameter, forming a thrust end with the possibility of capturing and holding the string drill pipes during descent and retrieval from the well.

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