阅读说明：本技术 阀式水力振荡器 (Valve type hydraulic oscillator ) 是由 柳贡慧 汪伟 李军 查春青 陈添 于 2020-06-11 设计创作，主要内容包括：本发明公开了一种阀式水力振荡器,其涉及石油钻井设备技术领域,包括：振荡短节；阀式控制短节,包括:壳体；调节件,其包括：调节件外圆筒部,调节件内圆筒部,调节件内圆筒部的上端呈封堵状态,调节件内圆筒部与调节件外圆通部之间相连并形成第一流道,调节件内圆筒部具有第一通孔和第二通孔；第一弹性件,第一弹性件能使得调节件沿上下移动；静阀座；第一阀芯,第一阀芯与静阀座内圆筒部之间设置有第二弹性件；第二阀芯,第二阀芯与静阀座外圆筒部之间具有第三弹性件,第二阀芯的下方与第三流道相连通,第二阀芯的侧壁上开设有第四通孔。本申请在工作过程中不易造成零部件的损坏,从而能够有效延长阀式水力振荡器的使用寿命。(The invention discloses a valve type hydraulic oscillator, which relates to the technical field of petroleum drilling equipment and comprises the following components: oscillating the short section; the valve type control short joint comprises a shell; an adjustment member, comprising: the upper end of the inner cylinder part of the adjusting part is in a blocking state, the inner cylinder part of the adjusting part is connected with the outer through part of the adjusting part to form a first flow passage, and the inner cylinder part of the adjusting part is provided with a first through hole and a second through hole; the first elastic piece can enable the adjusting piece to move up and down; a static valve seat; a second elastic element is arranged between the first valve core and the inner cylindrical part of the static valve seat; and a third elastic element is arranged between the second valve core and the outer cylindrical part of the static valve seat, the lower part of the second valve core is communicated with the third flow channel, and a fourth through hole is formed in the side wall of the second valve core. The application is difficult for causing the damage of spare part in the course of the work to can effectively prolong valve formula hydraulic oscillator's life.)

1. A valve hydroscillator, comprising:

the oscillating nipple can generate reciprocating oscillation in the axial direction under the action of internal pressure fluctuation;

a valved control sub connected to the oscillation sub, the valved control sub comprising:

a housing;

an adjustment member disposed in the housing, comprising: the adjusting part outer cylindrical part is at least partially arranged in the adjusting part inner cylindrical part in the adjusting part outer cylindrical part in a penetrating mode, the upper end of the adjusting part inner cylindrical part is in a blocking state, the outer side wall of the adjusting part inner cylindrical part is connected with the inner side wall of the adjusting part outer cylindrical part to form a first flow channel, and a first through hole and a second through hole located below the first through hole are formed in the side wall of the adjusting part inner cylindrical part;

a first elastic member provided between the adjusting member and the housing, the first elastic member being capable of moving the adjusting member up and down;

a static valve seat, the static valve seat comprising: the static valve seat outer cylindrical part is fixed with the shell, and a third flow passage is formed between the static valve seat outer cylindrical part and the shell; a static valve seat inner cylindrical part penetrating through the static valve seat outer cylindrical part, wherein a second flow passage is formed between the static valve seat outer cylindrical part and the static valve seat inner cylindrical part and is partially connected together, the second flow passage can be communicated with the inside of the adjusting part inner cylindrical part through the first through hole, a third through hole communicated with the third flow passage is formed at the joint of the static valve seat outer cylindrical part and the static valve seat inner cylindrical part, and the second through hole can be communicated with the third through hole;

a first valve core arranged in the inner cylinder part of the static valve seat, wherein a second elastic element is arranged between the first valve core and the inner cylinder part of the static valve seat so as to enable the first valve core to move up and down;

the second valve core is arranged in the outer cylinder part of the static valve seat and positioned below the first valve core, a third elastic part is arranged between the second valve core and the outer cylinder part of the static valve seat so that the second valve core can move up and down, the lower part of the second valve core is communicated with the third flow channel, and a fourth through hole is formed in the side wall of the second valve core so that the inner part of the second valve core is communicated with the second flow channel.

2. The valved hydroscillator of claim 1, wherein said housing comprises: the inner wall side of the upper joint is provided with a first step, the outer side wall of the upper end of the adjusting part is provided with an outer edge of the adjusting part, a first annular space is formed between the first step and the outer edge of the adjusting part, the first elastic part is arranged in the first annular space, and two ends of the first elastic part respectively abut against the first step and the outer edge of the adjusting part; the inner wall of the connecting cylinder is provided with an annular bulge, the outer side wall of the upper end of the outer cylinder part of the static valve seat is provided with the outer edge of the outer cylinder part of the static valve seat, and the outer edge of the outer cylinder part of the static valve seat is clamped between the annular bulge and the lower end of the upper joint to limit; the upper end of the lower joint extends into the connecting cylinder and abuts against the outer cylindrical part of the static valve seat.

3. The valved hydroscillator of claim 2, wherein said second spool is externally sleeved with a spool seat, a fourth resilient member and a lower retainer ring in sequence, said spool seat having a spool seat cylindrical portion, a radially extending outer spool seat boss at a lower end of said spool seat cylindrical portion, and a spool seat boss on a sidewall of said outer spool seat boss, wherein a gap is formed between adjacent said spool seat bosses, said outer spool seat boss abuts against said outer stationary seat cylindrical portion, said spool seat cylindrical portion is between said outer stationary seat cylindrical portion and said second spool and abuts against said third resilient member, a lower end of said lower retainer ring abuts against an upper end of said lower adaptor, said lower retainer ring having a lower retainer ring inner ring portion and a lower retainer ring boss on a sidewall of said lower retainer ring inner ring portion, wherein a gap is formed between said retainer ring bosses, and said third flow channel passes through said gap between adjacent said spool seat bosses, The gap between the raised parts of the retainer ring is communicated with the lower part of the second valve core; the lower end of the second valve core is connected with a second valve core ring which can prop against the lower retainer ring.

4. The valved hydroscillator of claim 1, wherein the upper end of the second spool has a radially extending second spool outer edge having a fifth throughbore therein, such that the third flow passage communicates with the interior of the second spool through the fifth throughbore and the fourth throughbore.

5. The valved hydroscillator of claim 1 wherein said first spool is substantially cylindrical, said first spool having a radially extending first spool outer land on a sidewall thereof, said first spool having a first spool ring attached to a lower end thereof, said stationary spool inner cylindrical portion having a radially extending inner edge on a lower end thereof, said inner edge being positioned between said first spool ring and said first spool outer land, said first spool outer land and said stationary spool inner cylindrical portion inner edge having a second annular space therebetween, said second elastomeric member being positioned in said second annular space, said second elastomeric member abutting said first spool outer land and said stationary spool inner edge, respectively.

6. The valved hydroscillator of claim 1, wherein said oscillation sub comprises: the sliding mandrel is arranged in the transmission joint and the short section shell in a penetrating manner, the outer side wall of the upper end of the supporting joint is connected with the inner side wall of the lower end of the short section shell, a second step is arranged on the side wall of the sliding mandrel, the disc spring is sleeved on the sliding mandrel, the piston mechanism is connected to the lower end of the transmission mandrel, the lower end of the disc spring can abut against the upper ends of the piston mechanism and the supporting joint, the upper end of the disc spring can abut against the lower end of the transmission joint and the second step, and the sliding mandrel and the transmission joint can slide relatively;

the piston mechanism includes: the piston ring fixing device comprises a hollow piston shaft seat connected with the lower end of the transmission mandrel, a piston ring sleeved on the piston shaft seat and a gland nut for fixing the piston ring, wherein the outer side of the piston ring is attached to the support joint.

7. The valved hydroscillator of claim 6, wherein the side wall of the sliding mandrel has a third step above the second step, a fourth step above the third step, a fifth step matching the third step is provided on the inner side wall of the drive joint, a groove is provided on the side wall of the sliding mandrel between the fourth step and the third step, and a sealing ring is provided in the groove.

Technical Field

The invention relates to the technical field of petroleum drilling equipment, in particular to a valve type hydraulic oscillator.

Background

With the development of the petroleum industry, in order to meet the development of unconventional oil and gas resources, the use proportion of horizontal wells and extended reach wells is continuously improved. However, in horizontal wells and extended reach wells, the contact area between the wellbore and the wellbore wall is continuously increased, so that the friction resistance is continuously increased, and finally, a 'pressure support' phenomenon may be formed, the drilling pressure cannot be transmitted to a drill bit, the mechanical drilling speed is low, and the drilling cost is high; and meanwhile, the conditions such as pressure building and drill tripping can occur, the target rate and the borehole quality of the horizontal well and the extended reach well are seriously affected, and the conditions are also an important factor for restricting the technical development of the horizontal well and the extended reach well. In a way to solve these problems, it is possible to add downhole mechanical devices on the drill string that are capable of producing certain expected vibrations, which have developed rapidly in recent years. One of the downhole mechanical devices is a hydraulic oscillator, and the hydraulic oscillator is introduced into a downhole drill string to enable the drill string to generate periodic vibration with certain frequency and amplitude, so that static friction of the drill string in the feeding process is changed into dynamic friction, and the downhole mechanical device has obvious advantages in the aspects of reducing friction resistance in the feeding process, improving the mechanical drilling speed, increasing the horizontal footage and shortening the drilling period.

Disclosure of Invention

The hydraulic oscillator at present generally mainly comprises power nipple joint, valve shaft assembly and oscillation nipple joint, and wherein, the power nipple joint mainly includes turbine motor or screw motor, and the valve shaft assembly includes dynamic valve piece and quiet valve piece, and dynamic valve piece closely cooperates with quiet valve piece terminal surface. In the working process of the hydraulic oscillator, a turbine motor or a screw motor in the power nipple drives a movable valve plate to rotate continuously, the movable valve plate reciprocates on the upper end face of a static valve plate to change the flow area of a flow channel continuously, so that the pressure in the tool flow channel fluctuates, and the oscillation nipple is driven to generate reciprocating thrust on a drill string. However, in the hydraulic oscillator with the structure, the end faces of the movable valve plate and the fixed valve plate are tightly attached in the working process, and the abrasion is serious, so that the service life of a tool is short. Moreover, when the drive nipple joint is screw motor, because there is certain vibration at the axial in the rotor of screw motor working process, can drive the valve block and collide with quiet valve block, this can lead to the valve block to damage, and the instrument is inefficacy.

In order to overcome the above-mentioned defects in the prior art, embodiments of the present invention provide a valve type hydraulic oscillator, which is less prone to damage of components during operation compared to the prior art, so that the service life of the valve type hydraulic oscillator can be effectively prolonged.

The specific technical scheme of the embodiment of the invention is as follows:

a valve hydroscillator, comprising:

the oscillating nipple can generate reciprocating oscillation in the axial direction under the action of internal pressure fluctuation;

a valved control sub connected to the oscillation sub, the valved control sub comprising:

a housing;

an adjustment member disposed in the housing, comprising: the adjusting part outer cylindrical part is at least partially arranged in the adjusting part inner cylindrical part in the adjusting part outer cylindrical part in a penetrating mode, the upper end of the adjusting part inner cylindrical part is in a blocking state, the outer side wall of the adjusting part inner cylindrical part is connected with the inner side wall of the adjusting part outer cylindrical part to form a first flow channel, and a first through hole and a second through hole located below the first through hole are formed in the side wall of the adjusting part inner cylindrical part;

a first elastic member provided between the adjusting member and the housing, the first elastic member being capable of moving the adjusting member up and down;

a static valve seat, the static valve seat comprising: the static valve seat outer cylindrical part is fixed with the shell, and a third flow passage is formed between the static valve seat outer cylindrical part and the shell; a static valve seat inner cylindrical part penetrating through the static valve seat outer cylindrical part, wherein a second flow passage is formed between the static valve seat outer cylindrical part and the static valve seat inner cylindrical part and is partially connected together, the second flow passage can be communicated with the inside of the adjusting part inner cylindrical part through the first through hole, a third through hole communicated with the third flow passage is formed at the joint of the static valve seat outer cylindrical part and the static valve seat inner cylindrical part, and the second through hole can be communicated with the third through hole;

a first valve core arranged in the inner cylinder part of the static valve seat, wherein a second elastic element is arranged between the first valve core and the inner cylinder part of the static valve seat so as to enable the first valve core to move up and down;

the second valve core is arranged in the outer cylinder part of the static valve seat and positioned below the first valve core, a third elastic part is arranged between the second valve core and the outer cylinder part of the static valve seat so that the second valve core can move up and down, the lower part of the second valve core is communicated with the third flow channel, and a fourth through hole is formed in the side wall of the second valve core so that the inner part of the second valve core is communicated with the second flow channel.

Preferably, the housing comprises: the inner wall side of the upper joint is provided with a first step, the outer side wall of the upper end of the adjusting part is provided with an outer edge of the adjusting part, a first annular space is formed between the first step and the outer edge of the adjusting part, the first elastic part is arranged in the first annular space, and two ends of the first elastic part respectively abut against the first step and the outer edge of the adjusting part; the inner wall of the connecting cylinder is provided with an annular bulge, the outer side wall of the upper end of the outer cylinder part of the static valve seat is provided with the outer edge of the outer cylinder part of the static valve seat, and the outer edge of the outer cylinder part of the static valve seat is clamped between the annular bulge and the lower end of the upper joint to limit; the upper end of the lower joint extends into the connecting cylinder and abuts against the outer cylindrical part of the static valve seat.

Preferably, a valve core seat, a fourth elastic element and a lower retainer ring are sequentially sleeved outside the second valve core, the valve core seat is provided with a valve core seat cylindrical portion, a radially extending valve core seat outer boss positioned at the lower end of the valve core seat cylindrical portion, and a valve core seat protruding portion positioned on the side wall of the valve core seat outer boss, a gap is formed between adjacent valve core seat protruding portions, the valve core seat outer boss abuts against the static valve seat outer cylindrical portion, the valve core seat cylindrical portion is positioned between the static valve seat outer cylindrical portion and the second valve core and abuts against the third elastic element, the lower end of the lower retainer ring abuts against the upper end of the lower joint, the lower retainer ring is provided with a lower retainer ring inner ring portion and a lower retainer ring protruding portion positioned on the side wall of the lower retainer ring inner ring portion, a gap is formed between the retainer ring protruding portions, and the third flow channel passes through the gap between adjacent valve core, The gap between the raised parts of the retainer ring is communicated with the lower part of the second valve core; the lower end of the second valve core is connected with a second valve core ring which can prop against the lower retainer ring.

Preferably, the upper end of the second valve core has a second valve core outer edge extending along the radial direction, and the second valve core outer edge has a fifth through hole, so that the third flow channel is communicated with the inside of the second valve core through the fifth through hole and the fourth through hole.

Preferably, the first valve core is substantially in a cylindrical state, a first valve core outer boss extending in the radial direction is arranged on the side wall of the first valve core, a first valve core ring is connected to the lower end of the first valve core, a static valve seat inner cylindrical portion inner edge extending in the radial direction is arranged at the lower end of the static valve seat inner cylindrical portion, the inner edge is located between the first valve core ring and the first valve core outer boss, a second annular space is arranged between the first valve core outer boss and the static valve seat inner cylindrical portion inner edge, the second elastic member is located in the second annular space, and the second elastic member respectively abuts against the first valve core outer boss and the static valve seat inner cylindrical portion inner edge.

Preferably, the oscillating sub comprises: the sliding mandrel is arranged in the transmission joint and the short section shell in a penetrating manner, the outer side wall of the upper end of the supporting joint is connected with the inner side wall of the lower end of the short section shell, a second step is arranged on the side wall of the sliding mandrel, the disc spring is sleeved on the sliding mandrel, the piston mechanism is connected to the lower end of the transmission mandrel, the lower end of the disc spring can abut against the upper ends of the piston mechanism and the supporting joint, the upper end of the disc spring can abut against the lower end of the transmission joint and the second step, and the sliding mandrel and the transmission joint can slide relatively;

the piston mechanism includes: the piston ring fixing device comprises a hollow piston shaft seat connected with the lower end of the transmission mandrel, a piston ring sleeved on the piston shaft seat and a gland nut for fixing the piston ring, wherein the outer side of the piston ring is attached to the support joint.

Preferably, the side wall of the sliding mandrel is provided with a third step located above the second step and a fourth step located above the third step, the inner side wall of the transmission joint is provided with a fifth step matched with the third step, a groove is formed in the side wall of the sliding mandrel between the fourth step and the third step, and a sealing ring is arranged in the groove.

The technical scheme of the invention has the following remarkable beneficial effects:

valve formula hydraulic oscillator in this application passes through the hydraulic drive adjusting part of drilling fluid, first case and second case and produces the slip, and then makes the area of overflowing of the runner between first case and the second case be periodic variation, by little to big, by big to little again, constantly forms the water hammer pressure wave, and the pressure wave upwards transmits to the oscillation nipple joint to make the oscillation nipple joint produce reciprocal oscillation in the axial under the pressure oscillation effect. Therefore, the static friction resistance between the drill string with the valve type hydraulic oscillator and the well wall is overcome, namely the static friction between the drill string positioned above the valve type hydraulic oscillator and the well wall is converted into the dynamic friction, the friction resistance is reduced, the loss of the bit pressure is effectively reduced, and the transmission efficiency of the bit pressure is improved. Valve formula hydraulic oscillator in this application has saved turbine or screw drive nipple joint, has effectively reduced instrument length, improves instrument range of application. Meanwhile, the valve type control short section has a drilling fluid starting flow, and the tool does not work under the condition of small flow in the tripping stage, so that the time of the tool oscillation short section for pure drilling is ensured. The flow is increased in the drilling process, the valve type control short section starts to work, the second valve core oscillates in a reciprocating mode to change the flow area of a flow channel between the first valve core and the second valve core, the first valve core and the second valve core can be out of contact in the working process, and therefore the first valve core and the second valve core cannot collide and wear, the service life of the valve cores can be effectively prolonged, and the service life of the whole tool is prolonged.

Specific embodiments of the present invention are disclosed in detail with reference to the following description and drawings, indicating the manner in which the principles of the invention may be employed. It should be understood that the embodiments of the invention are not so limited in scope. The embodiments of the invention include many variations, modifications and equivalents within the spirit and scope of the appended claims. Features that are described and/or illustrated with respect to one embodiment may be used in the same way or in a similar way in one or more other embodiments, in combination with or instead of the features of the other embodiments.

Drawings

The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way. In addition, the shapes, the proportional sizes, and the like of the respective members in the drawings are merely schematic for facilitating the understanding of the present invention, and do not specifically limit the shapes, the proportional sizes, and the like of the respective members of the present invention. Those skilled in the art, having the benefit of the teachings of this invention, may choose from the various possible shapes and proportional sizes to implement the invention as a matter of case.

FIG. 1 is a schematic diagram of a valve type hydroscillator according to an embodiment of the present invention;

FIG. 2 is a schematic structural diagram of a valve type control nipple in an embodiment of the invention;

FIG. 3 is a schematic structural diagram of a sliding mandrel in an oscillation pup joint in the embodiment of the invention;

FIG. 4 is a schematic structural diagram of an adjusting member of the valve type control nipple in the embodiment of the invention;

FIG. 5 is a schematic structural view of a static valve seat in an embodiment of the present invention;

FIG. 6 is a schematic structural diagram of a first valve spool according to an embodiment of the present invention;

FIG. 7 is a schematic structural diagram of a second valve spool according to an embodiment of the present invention;

FIG. 8 is a schematic structural view of a valve cartridge seat according to an embodiment of the present invention;

fig. 9 is a schematic structural diagram of a lower retainer ring in the embodiment of the present invention.

Reference numerals of the above figures:

1. oscillating the short section; 2. connecting short sections; 3. a valve type control short joint; 101. sliding the mandrel; 1011. a second step; 1012. a third step; 1013. a fourth step; 1014. a groove; 1015. an external spline; 102. A drive joint; 1021. a fifth step; 103. a nipple shell; 104. a disc spring; 105. a piston mechanism; 1051. a piston shaft seat; 1052. a piston ring; 1053. a compression nut; 106. a support joint; 107. adjusting the cylinder; 301. an upper joint; 3011. a first step; 302. an adjustment member; 3021. the outer edge of the regulating part; 3022. an adjustment member outer cylindrical portion; 3023. an inner cylindrical adjustment member portion; 3024. a first flow passage; 3025. a first through hole; 3026. a second through hole; 303. a first elastic member; 304. a connecting cylinder; 305. a static valve seat; 3051. a static valve seat outer cylindrical portion; 3052. a static valve seat inner cylindrical portion; 3053. the outer edge of the outer cylindrical part of the static valve seat; 3054. a second flow passage; 3055. a third through hole; 3056. the inner edge of the inner cylindrical part of the static valve seat; 306. a first valve spool; 3061. a first valve core outer boss; 3062. a first spool core ring; 307. a second elastic member; 308. a second valve core; 3081. The outer edge of the second valve core; 3082. a fifth through hole; 3083. a second spool core ring; 3084. a fourth via hole; 309. a third elastic member; 310. a valve core seat; 3101. a valve core seat cylindrical portion; 3102. a valve core seat outer boss; 3103. a valve core seat boss; 311. a fourth elastic member; 312. a lower retainer ring; 3121. an inner ring part of the lower retainer ring; 3122. a lower retainer ring boss; 313. a lower joint; 314. a first annular space; 315. a second annular space; 316. and a third flow passage.

Detailed Description

The details of the present invention can be more clearly understood in conjunction with the accompanying drawings and the description of the embodiments of the present invention. However, the specific embodiments of the present invention described herein are for the purpose of illustration only and are not to be construed as limiting the invention in any way. Any possible variations based on the present invention may be conceived by the skilled person in the light of the teachings of the present invention, and these should be considered to fall within the scope of the present invention. It will be understood that when an element is referred to as being "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "mounted," "connected," and "connected" are to be construed broadly and may include, for example, mechanical or electrical connections, communications between two elements, direct connections, indirect connections through intermediaries, and the like. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like as used herein are for illustrative purposes only and do not denote a unique embodiment.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein in the description of the present application is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

Compared with the prior art, in order to prevent parts from being damaged easily during working and effectively prolong the service life of the valve type hydraulic oscillator, the present application provides a valve type hydraulic oscillator, where fig. 1 is a schematic structural diagram of the valve type hydraulic oscillator in an embodiment of the present invention, fig. 2 is a schematic structural diagram of the valve type control nipple in an embodiment of the present invention, and as shown in fig. 1 and fig. 2, the valve type hydraulic oscillator may include: the oscillation nipple 1, the oscillation nipple 1 can produce the reciprocating oscillation in the axial under the internal pressure fluctuation; the valve type control short joint 3 is connected with the oscillation short joint 1, and the valve type control short joint 3 comprises a shell; an adjustment member 302 disposed in the housing, comprising: an adjusting member outer cylindrical portion 3022, an adjusting member inner cylindrical portion 3023 at least partially inserted into the adjusting member outer cylindrical portion 3022, an upper end of the adjusting member inner cylindrical portion 3023 being in a closed state, an outer side wall of the adjusting member inner cylindrical portion 3023 being connected to an inner side wall of the adjusting member outer cylindrical portion to form a first flow passage 3024, and the adjusting member inner cylindrical portion 3023 having a first through hole 3025 and a second through hole 3026 formed in a side wall thereof and located below the first through hole 3025; a first elastic member 303 disposed between the adjusting member 302 and the housing, the first elastic member 303 being capable of moving the adjusting member 302 up and down; a static valve seat 305, the static valve seat 305 comprising: a stationary seat outer cylindrical portion 3051, the stationary seat outer cylindrical portion 3051 being fixed to the housing, and a third flow passage 316 being formed between the stationary seat outer cylindrical portion 3051 and the housing; a static valve seat inner cylindrical part 3052 penetrating the static valve seat outer cylindrical part 3051, a second flow channel 3054 is formed between the static valve seat outer cylindrical part 3051 and the static valve seat inner cylindrical part 3052 and is partially connected together, the second flow channel 3054 can be communicated with the inside of the adjusting part inner cylindrical part 3023 through a first through hole 3025, a third through hole 3055 communicated with the third flow channel 316 is formed at the joint of the static valve seat outer cylindrical part 3051 and the static valve seat inner cylindrical part 3052, and the second through hole 3026 can be communicated with the third through hole 3055; a first valve body 306 provided in the stationary seat inner cylindrical portion 3052, and a second elastic member 307 provided between the first valve body 306 and the stationary seat inner cylindrical portion 3052 to allow the first valve body 306 to move up and down; a second valve body 308 provided in the stationary seat outer cylinder part 3051 and located below the first valve body 306, a third elastic member 309 provided between the second valve body 308 and the stationary seat outer cylinder part 3051 to allow the second valve body 308 to move up and down, a third flow path 316 communicating with a lower portion of the second valve body 308, and a fourth through hole 3084 provided in a side wall of the second valve body 308 to allow the second flow path 3054 to communicate with an inside of the second valve body 308.

Valve formula hydraulic oscillator in this application passes through hydraulic drive adjusting part 302, first case 306 and the second case 308 production slip of drilling fluid, and then makes the area of overflowing of the runner between first case 306 and the second case 308 be periodic variation, by little to big, again by big to little, constantly forms the water hammer pressure wave, and the pressure wave upwards transmits to oscillation nipple 1 to make oscillation nipple 1 produce reciprocal oscillation in the axial under the pressure oscillation effect. Therefore, the static friction resistance between the drill string with the valve type hydraulic oscillator and the well wall is overcome, namely the static friction between the drill string positioned above the valve type hydraulic oscillator and the well wall is converted into the dynamic friction, the friction resistance is reduced, the loss of the bit pressure is effectively reduced, and the transmission efficiency of the bit pressure is improved. Valve formula hydraulic oscillator in this application has saved turbine or screw drive nipple joint, has effectively reduced instrument length, improves instrument range of application. Meanwhile, the valve type control nipple 3 has a drilling fluid starting flow, and a tool does not work under the condition of small flow in the tripping stage, so that the time of the tool oscillation nipple 1 for pure drilling is ensured. During the drilling process, the flow is increased, the valve type control short joint 3 starts to work, the second valve core 308 oscillates in a reciprocating mode to change the flow area of a flow channel between the first valve core 306 and the second valve core 308, and the first valve core 306 and the second valve core 308 can be in no contact with each other during the working process, so that the first valve core 306 and the second valve core 308 cannot collide and wear, the service life of the valve cores can be effectively prolonged, and the service life of the whole tool is prolonged.

To better understand the valved hydroscillator of the present application, it will be further explained and illustrated. As shown in fig. 1, the valved hydroscillator may comprise: the oscillation nipple 1, the oscillation nipple 1 can produce the reciprocating oscillation in the axial under the internal pressure fluctuation; and the valve type control nipple 3 is connected with the oscillation nipple 1, and the valve type control nipple 3 is used for generating hydraulic pressure fluctuation under the hydraulic drive of the drilling fluid. The interior of the oscillating sub 1 communicates with the interior of the valved sub 3, and in general, the oscillating sub 1 is located above the valved sub 3. In order to facilitate the connection between the oscillation nipple 1 and the valve type control nipple 3, the oscillation nipple and the valve type control nipple can be connected together through a connecting nipple 2.

Fig. 3 is a schematic structural diagram of a sliding mandrel in an oscillation sub according to an embodiment of the present invention, and as shown in fig. 1 and fig. 3, the oscillation sub 1 may include: sliding mandrel 101, transmission joint 102, nipple housing 103, disc spring 104, piston mechanism 105 and support joint 106. The outer side wall of the lower end of the transmission joint 102 is in threaded connection with the inner side wall of the upper end of the nipple shell 103, and the inner diameter of the lower end of the transmission joint 102 is smaller than that of the upper end of the nipple shell 103. The sliding mandrel 101 is arranged in the transmission joint 102 and the nipple housing 103 in a penetrating manner, and the sliding mandrel 101 and the transmission joint 102 can slide relatively. The outer side wall of the upper end of the supporting joint 106 is connected with the inner side wall of the lower end of the nipple shell 103, and the inner diameter of the upper end of the supporting joint 106 is smaller than that of the lower end of the nipple shell 103. The side wall of the sliding core shaft 101 is provided with a second step 1011, the disc spring 104 is sleeved on the sliding core shaft 101, the piston mechanism 105 is connected to the lower end of the transmission core shaft, the lower end of the disc spring 104 can abut against the upper ends of the piston mechanism 105 and the support joint 106, and the upper end of the disc spring 104 can abut against the lower end of the transmission joint 102 and the second step 1011.

In a possible embodiment, as shown in fig. 1, an adjusting cylinder 107 is sleeved outside the sliding mandrel 101, the upper end of the adjusting cylinder 107 abuts against the transmission joint 102, and the lower end abuts against the disc spring 104, and the compression amount of the disc spring 104 can be adjusted by adjusting the length of the adjusting cylinder 107, so as to control the oscillation amplitude of the oscillating nipple 1.

As shown in fig. 1, the piston mechanism 105 may include: the piston rod comprises a hollow piston shaft seat 1051 connected with the lower end of the transmission mandrel, a piston ring 1052 sleeved on the piston shaft seat 1051 and a compression nut 1053 for fixing the piston ring 1052, wherein the outer side of the piston ring 1052 is attached to the support joint 106. The hollow piston shaft seat 1051 is communicated with the inside of the sliding mandrel 101, and the outer diameter of the piston shaft seat 1051 is larger than the outer diameter of the lower end of the sliding mandrel 101, so that the piston shaft seat can abut against the disc spring 104. A compression nut 1053 is screwed on the lower end of the piston shaft seat 1051 to fix the piston ring 1052 up and down. When the pressure of the drilling fluid below the piston mechanism 105 increases, the pressure of the drilling fluid acts on the lower piston ring 1052, thereby driving the entire sliding mandrel 101 to compress the disc spring 104 to move upward. When the pressure of the drilling fluid below the piston mechanism 105 is reduced again, the whole sliding mandrel 101 is driven to move downwards under the action of the disc spring 104, and in such a circulation manner, the oscillation nipple 1 generates reciprocating oscillation in the axial direction under the action of pressure fluctuation.

As shown in fig. 1 and 3, the side wall of the sliding core shaft 101 has a third step 1012 located above the second step 1011 and a fourth step 1013 located above the third step 1012, and the inner side wall of the transmission joint 102 has a fifth step 1021 matching with the third step 1012, and after the sliding core shaft 101 moves downward to a certain extent, the fifth step 1021 can abut against the third step 1012 to prevent the sliding core shaft 101 from further moving downward, so as to realize a limiting effect. The side wall of the sliding mandrel 101 between the fourth step 1013 and the third step 1012 is provided with a groove 1014, and a sealing ring is arranged in the groove 1014, and the outer side of the sealing ring is abutted against the inner side wall of the transmission joint 102, so that the sealing between the sliding mandrel 101 and the transmission joint 102 can be realized. The third step 1012 on the outer side of the sliding mandrel 101 is provided with an external spline 1015, the fifth step 1021 of the transmission joint 102 is provided with an internal spline, and the external spline 1015 is matched with the internal spline, so that relative sliding between the sliding mandrel 101 and the transmission joint 102 can be realized, relative rotation cannot be found between the sliding mandrel 101 and the transmission joint 102, and separation between the sliding mandrel 101 and a part connected with the upper end is prevented.

Fig. 2 is a schematic structural diagram of the valved control sub according to an embodiment of the present invention, and as shown in fig. 2, the valved control sub 3 may include a housing, an adjusting member 302, a first elastic member 303, a static valve seat 305, a first valve core 306, and a second valve core 308. A housing, the housing may include: an upper connector 301, a connector barrel 304 connected to the upper connector 301, and a lower connector 313 connected to the connector barrel 304.

An adjusting member 302 is arranged in the housing, fig. 4 is a schematic structural diagram of the adjusting member of the valve type control sub in the embodiment of the present invention, and as shown in fig. 4, the adjusting member 302 may include: an adjusting member outer cylindrical portion 3022, an adjusting member inner cylindrical portion 3023 at least partially inserted into the adjusting member outer cylindrical portion 3022, an upper end of the adjusting member inner cylindrical portion 3023 is closed, an outer side wall of the adjusting member inner cylindrical portion 3023 is connected to an inner side wall of the adjusting member outer cylindrical portion to form a first flow passage 3024, and the adjusting member inner cylindrical portion 3023 has a first through hole 3025 and a second through hole 3026 below the first through hole 3025 on the side wall.

As shown in fig. 2, a first elastic member 303 is provided between the adjusting member 302 and the housing, and the first elastic member 303 enables the adjusting member 302 to move up and down. The inner wall side of the upper joint 301 is provided with a first step 3011, as shown in fig. 4, the upper end outer side wall of the adjusting piece 302 is provided with an adjusting piece outer edge 3021, a first annular space 314 is formed between the first step 3011 and the adjusting piece outer edge 3021, the first elastic piece 303 is arranged in the first annular space 314, and two ends of the first elastic piece 303 respectively abut against the first step 3011 and the adjusting piece outer edge 3021. The upper joint 301 may be opened with an opening communicating with the first annular space 314, so that when the first elastic member 303 is compressed, the gas or liquid in the first annular space 314 can be discharged. The first elastic member 303 may generally be a spring.

Fig. 5 is a schematic structural diagram of a static valve seat in an embodiment of the present invention, and as shown in fig. 5, the static valve seat 305 may include: a stationary seat outer cylindrical portion 3051, the stationary seat outer cylindrical portion 3051 being fixed to the housing, and a third flow passage 316 being formed between the stationary seat outer cylindrical portion 3051 and the housing; a stationary seat inner cylindrical portion 3052 inserted into the stationary seat outer cylindrical portion 3051, a second flow path 3054 formed between the stationary seat outer cylindrical portion 3051 and the stationary seat inner cylindrical portion 3052, and partially connected to each other, the second flow path 3054 being communicable with the inside of the adjuster inner cylindrical portion 3023 through a first through hole 3025, and a third through hole 3055 being communicable with the third flow path 316 being provided at a junction of the stationary seat outer cylindrical portion 3051 and the stationary seat inner cylindrical portion 3052. When the adjusting member 302 is moved downward, the second through hole 3026 can communicate with the third through hole 3055.

As shown in fig. 2, the inner wall of the connecting cylinder 304 has an annular protrusion, the outer side wall of the upper end of the static valve seat outer cylinder part 3051 has an outer edge 3053 of the static valve seat outer cylinder part, and the outer edge 3053 of the static valve seat outer cylinder part is caught between the annular protrusion and the lower end of the upper joint 301 to be restricted.

As shown in fig. 2, the first valve body 306 is provided in the stationary seat inner cylindrical portion 3052, and a second elastic member 307 is provided between the first valve body 306 and the stationary seat inner cylindrical portion 3052 so that the first valve body 306 can move up and down. The second elastic member 307 may be a spring. Specifically, fig. 6 is a schematic structural diagram of the first valve core in the embodiment of the present invention, as shown in fig. 2 and 6, the first valve core 306 is substantially in a cylindrical state, a side wall of the first valve core 306 has a first valve core outer boss 3061 extending in the radial direction, the lower end of the first valve core 306 is connected with a first valve core ring 3062, the lower end of the static valve seat inner cylindrical portion 3052 has a static valve seat inner cylindrical portion inner edge 3056 extending in the radial direction, the inner edge is located between the first valve core ring 3062 and the first valve core outer boss 3061, a second annular space 315 is provided between the first valve core outer boss 3061 and the static valve seat inner cylindrical portion inner edge 3056, the second elastic member 307 is located in the second annular space 315, and the second elastic member 307 abuts against the first valve core outer boss 3061 and the static valve seat inner cylindrical portion inner edge 3056, respectively. When the first valve spool 306 moves upward to a certain extent, the lower end of the adjuster inner cylindrical portion 3023 can abut against the upper end of the first valve spool 306. In this way, the first valve body 306 and the stationary seat inner cylindrical portion 3052 can reciprocate up and down by the second elastic member 307, and the position of the reciprocating up and down is restricted and controlled.

As shown in fig. 2, the second valve body 308 is provided in the stationary seat outer cylindrical portion 3051 below the first valve body 306, and a third elastic member 309 is provided between the second valve body 308 and the stationary seat outer cylindrical portion 3051 so that the second valve body 308 can move up and down, and the lower side of the second valve body 308 communicates with the third flow channel 316. A fourth through hole 3084 is formed on a side wall of the second valve core 308 to communicate the inside of the second valve core 308 with the second flow channel 3054. Fig. 7 is a schematic structural diagram of the second valve element according to the embodiment of the present invention, and as shown in fig. 7, the upper end of the second valve element 308 has a second valve element outer edge 3081 extending in the radial direction, and the second valve element outer edge 3081 has a fifth through hole 3082, so that the third flow channel 316 communicates with the inside of the second valve element 308 through the fifth through hole 3082 and the fourth through hole 3084. The third elastic member 309 may be a spring in general. The lower end of the second valve core 308 is connected with a second valve core ring 3083 which can support the lower retainer 312

As shown in fig. 2, the upper end of the lower joint 313 protrudes into the connecting cylinder 304 and abuts against the stationary seat outer cylindrical portion 3051. In one possible embodiment, in order to enable the lower portion of the second valve element 308 to communicate with the third flow passage 316, the second valve element 308 is sleeved with a valve element seat 310, a fourth elastic element 311 and a lower retainer 312 in sequence. Fig. 8 is a schematic structural diagram of the valve seat in the embodiment of the present invention, as shown in fig. 8, the valve seat 310 has a valve seat cylindrical portion 3101, a radially extending valve seat outer boss 3102 located at a lower end of the valve seat cylindrical portion 3101, a valve seat boss 3103 located on a side wall of the valve seat outer boss 3102, a gap is formed between adjacent valve seat bosses 3103, the valve seat outer boss 3102 abuts against the static valve seat outer cylindrical portion 3051, the valve seat cylindrical portion 3101 is located between the static valve seat outer cylindrical portion 3051 and the second valve core 308 and abuts against the third elastic member 309, and a lower end of the lower retainer 312 abuts against an upper end of the lower joint 313. Fig. 9 is a schematic structural view of the lower retainer ring in the embodiment of the present invention, and as shown in fig. 9, the lower retainer ring 312 has a lower retainer ring inner ring portion 3121 and lower retainer ring protruding portions 3122 located on a side wall of the lower retainer ring inner ring portion 3121, and gaps are provided between the retainer ring protruding portions. The third flow passage 316 communicates with the lower side of the second spool 308 through the gaps between the adjacent spool seat protrusions 3103 and the gaps between the retainer ring protrusions. In this way, the valve seat 310 is abutted against the third elastic member 309, and the third flow passage 316 can communicate with the lower side of the second valve spool 308 through the gap between the valve seat protrusions 3103 and the gap between the retainer ring protrusions. The fourth elastic member 311 is generally a disc spring 104 which plays a role of damping vibration, so that impact on the housing generated when the second spool 308 reciprocates can be effectively reduced.

Since the adjuster 302 can compress the first elastic member 303 to move downward, relative displacement can be generated between the adjuster 302 and the stationary valve seat 305. Therefore, the valved hydroscillator has at least two states, in the first state, the second through hole 3026 is closed by the static valve seat 305, and the first through hole 3025 is opened; in the second state, the static valve seat 305 blocks the first through hole 3025, and the second through hole 3026 communicates with the third through hole 3055.

The valve type hydraulic oscillator in the application works according to the following principle:

during the initial operation of the valve type hydraulic oscillator, drilling fluid flows down from the upper drill string to the valve type control nipple 3 through the sliding mandrel 101 of the oscillation nipple 1. Then flows into the lower drill string through the first flow passage 3024 of the adjusting member 302, the first through hole 3025, the first valve core 306, the second valve core 308 and the lower connector 313 in sequence, or flows into the lower drill string through the first flow passage 3024 of the adjusting member 302, the second flow passage 3054 of the static valve seat 305, the second valve core 308 and the lower connector 313 and then flows out through a drill bit nozzle into the drill string and the borehole wall annulus, so that a pressure difference is generated between the interior of the drill string and the annulus.

In the above process, the outer side wall of the inner cylindrical portion 3023 of the adjusting member, the inner side wall of the outer cylindrical portion 3022 of the adjusting member, the inner side wall of the upper joint 301 and the like together form a pressure chamber, the upper end surface of the adjusting member 302 is subjected to high pressure inside the drill string, the first annular space 314 formed between the first step 3011 and the outer edge 3021 of the adjusting member is connected with the outer annular space through the opening of the side wall of the upper joint 301 to be low pressure, and the adjusting member 302 moves downward to compress the first elastic member 303 under the action of the pressure difference.

When a drill bit at the lower end of the drill string is not in contact with the bottom of the well, the flow rate of drilling fluid is small, the pressure difference between the inside and the outside of the drill string is small, the downward thrust on the adjusting piece 302 is small, the downward movement distance of the adjusting piece 302 is small, the first valve core outer boss 3061 of the first valve core 306 is not contacted, meanwhile, the first through hole 3025 of the inner cylindrical part 3023 of the adjusting piece is communicated with the first flow channel 3024 at the upper end of the static valve seat 305, the fluid pressure at the upper end and the lower end of the first valve core 306 is balanced, the first valve core 306 does not move up.

When the drill bit contacts the bottom of the well and starts drilling, the flow of drilling fluid is increased to cause the pressure difference between the inside and the outside of the drill string to be increased, the downward thrust applied to the adjusting piece 302 is increased, the downward movement is continued to be contacted with the first valve core outer boss 3061 of the first valve core 306, the first valve core 306 is pushed to move downwards, and meanwhile, the second elastic piece 307 is compressed. When the lower end of the outer cylinder part 3022 of the adjusting element contacts the upper end surface of the stationary valve seat 305, the adjusting element 302 and the first valve core 306 move to the limiting position and stop moving, and at this time, the distance between the first valve core 306 and the second valve core 308 is the minimum, the flow passage area between the first valve core 306 and the second valve core 308 is the minimum, and the generated pressure drop is the maximum. The drilling fluid generates a pressure drop when flowing through the fifth through hole 3082 of the second valve core outer edge 3081 of the second valve core 308, and a pressure difference is generated between the upper end and the lower end of the second valve core outer edge 3081, so that the second valve core 308 is pushed to move downwards, and the third elastic element 309 is compressed. During the downward movement of the second valve core 308, the distance between the second valve core 308 and the first valve core 306 increases, and the flow area between the first valve core 306 and the second valve core 308 increases, so that the flow rate flowing through the fifth through hole 3082 of the outer edge 3081 of the second valve core decreases, and the thrust acting on the outer edge 3081 of the second valve core decreases. When the downward thrust of the drilling fluid is smaller than the upward thrust of the third elastic member 309, the second valve core 308 performs deceleration movement until the drilling fluid stops, at this time, the distance between the first valve core 306 and the second valve core 308 is the largest, the flow passage area is the largest, and the generated pressure drop is the smallest. Subsequently, the second valve core 308 moves upward to be reset under the action of the third elastic element 309, the distance between the second valve core 308 and the first valve core 306 is continuously reduced, when the upper end surface of the second valve core ring 3083 contacts with the lower retainer ring 312, the second valve core 308 reaches the limiting position and stops moving, and at the moment, the distance between the second valve core 308 and the first valve core 306 returns to the minimum distance.

Along with the periodic change of the flow passage area between the second valve core 308 and the first valve core 306, the water hammer pressure wave is continuously formed during the period from small to large and then from large to small, and is transmitted to the end surface of the piston ring 1052 of the oscillating nipple 1. When the flow area between the second valve core 308 and the first valve core 306 is the smallest, the pressure drop generated by the flowing of the drilling fluid is the largest, the lower end surface of the piston ring 1052 of the oscillating nipple 1 bears high pressure, the upper end surface is low pressure, and the piston ring 1052 pushes the sliding mandrel 101 to move upwards to extend out of the nipple shell 103 under the action of the pressure difference. At the moment, the sliding core shaft 101 moves upwards, the disc spring 104 is compressed at the same time, certain thrust is generated on a drill string above the valve type hydraulic oscillator so as to overcome static friction resistance between the drill string and the well wall, the drill string above the sliding core shaft 101 moves to a certain degree, the sliding core shaft 101 moves upwards to extend out of the short joint body 103, and thus the static friction force between the upper pipe string and the well wall is converted into dynamic friction force, the friction resistance is reduced, the loss of the drilling pressure is reduced, and the transmission efficiency of the drilling pressure is improved. When the flow area between the second valve core 308 and the first valve core 306 is the largest, the pressure drop generated by the flowing of the drilling fluid is the smallest, and the sliding core shaft 101 in the oscillating nipple 1 moves downwards to reset under the action of the disc spring 104. Therefore, under the action of periodic pressure fluctuation, the sliding core shaft 101 reciprocates axially to drive adjacent drill strings to do periodic reciprocating motion in a borehole, so that static friction of the drill strings at the bottom of the well is changed into dynamic friction, the frictional resistance is greatly reduced, the effective bit pressure applied to a drill bit is ensured, and the mechanical drilling speed is improved.

In the drilling completion tripping stage, the flow of drilling fluid is reduced, the pressure difference between the inside and the outside of the drill string is reduced, the downward thrust applied on the adjusting piece 302 is reduced, the adjusting piece 302 moves upwards and resets under the action of the first elastic piece 303, meanwhile, the first through hole 3025 on the inner cylinder part 3023 of the adjusting piece is opened, the second through hole 3026 is closed, the inside of the inner cylinder part 3023 of the adjusting piece is communicated with the low-pressure flow passage at the lower end of the second valve core 308 through the first through hole 3025 and the third flow passage 316 between the stationary valve seat 305 and the connecting cylinder 304, the fluid pressure at the end part of the first valve core 306 reaches a balanced state, the first valve core 306 moves upwards and resets under the action of the second elastic piece 307, and when the first valve core ring 3062 contacts with the lower end surface of the inner cylinder part of the stationary valve core seat 310, the first valve.

All articles and references disclosed, including patent applications and publications, are hereby incorporated by reference for all purposes. The term "consisting essentially of …" describing a combination shall include the identified element, ingredient, component or step as well as other elements, ingredients, components or steps that do not materially affect the basic novel characteristics of the combination. The use of the terms "comprising" or "including" to describe combinations of elements, components, or steps herein also contemplates embodiments that consist essentially of such elements, components, or steps. By using the term "may" herein, it is intended to indicate that any of the described attributes that "may" include are optional. A plurality of elements, components, parts or steps can be provided by a single integrated element, component, part or step. Alternatively, a single integrated element, component, part or step may be divided into separate plural elements, components, parts or steps. The disclosure of "a" or "an" to describe an element, ingredient, component or step is not intended to foreclose other elements, ingredients, components or steps.

The embodiments in the present specification are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other. The above embodiments are merely illustrative of the technical ideas and features of the present invention, and the purpose thereof is to enable those skilled in the art to understand the contents of the present invention and implement the present invention, and not to limit the protection scope of the present invention. All equivalent changes and modifications made according to the spirit of the present invention should be covered within the protection scope of the present invention.