A Hydraulic Oscillator for Three-Dimensional Multi-Directional Vibration in Horizontal Well Drilling

Abstract

The present invention relates to a hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling, which comprises a drill pipe connection part, a circumferential vibration part, an axial vibration part, a radial vibration part, a power part and a radio frequency part that are sequentially connected axially. The outer side wall of the drill pipe connection part is threadedly connected to the circumferential vibration part, and one end of the drill pipe connection part is elastically connected to the axial vibration part; the power part includes a single-head screw, a stator sleeve and a pressure stabilizing filter element, and the radial vibration part includes a moving valve seat; wherein, when the single-head screw rotates driven by the fluid in the clearance flow channel, the moving valve seat radially knocks the stator sleeve to generate radial vibration, and the flow area of the radio frequency flow channel changes periodically, so that the axial vibration part and the circumferential vibration part respectively perform axial vibration and circumferential vibration relative to the drill pipe connection part.

Description

Technical Field

[0001] The present invention relates to the technical field of drilling and development in the oil and gas industry, and particularly relates to a hydraulic oscillator with three-dimensional multi-directional vibration for horizontal well drilling. Background Art

[0002] With the continuous deepening of the development of unconventional oil and gas resources, horizontal wells have become the main well type for developing shale oil and gas. During the horizontal well drilling process, the bottom drill string contacts the lower well wall due to the action of gravity, generating a large frictional resistance, which causes the drilling pressure to be unable to be effectively transmitted, resulting in problems such as sticking and dragging. Sticking and dragging prevent the drilling pressure from being effectively transmitted to the drill bit, thereby reducing the mechanical drilling rate, increasing the drilling cycle, raising the drilling cost, and even making it difficult to guarantee the wellbore quality, leading to serious downhole accidents. The best way to solve sticking and dragging is to make the drill string generate high-frequency vibration, converting the static friction of the drill string into dynamic friction, thereby reducing the frictional resistance loss along the drill string. Most existing hydraulic oscillators generate pressure fluctuations by changing the flow area of the water eye, and use the compression and rebound of the spring under the action of the pressure fluctuation to generate axial vibration. Due to the single vibration direction, insufficient impact force and vibration displacement of such hydraulic oscillators, the problem of sticking and dragging during the sliding drilling of ultra-deep and ultra-long horizontal wells has not been effectively solved, and there is a lack of more room for improvement. Summary of the Invention

[0003] The present invention provides a hydraulic oscillator with three-dimensional multi-directional vibration for horizontal well drilling to solve one or several of the technical problems existing in the prior art.

[0004] The technical solution of the present invention to solve the above technical problems is as follows: A hydraulic oscillator with three-dimensional multi-directional vibration for horizontal well drilling, comprising a drill pipe connection part, a circumferential vibration part, an axial vibration part, a radial vibration part, a power part, and a radio frequency part connected in sequence axially. The outer side wall of the drill pipe connection part is threadedly connected to the circumferential vibration part, and one end of the drill pipe connection part is elastically connected to the axial vibration part;

[0005] The radial vibration part includes a moving valve seat. The power part includes a single-head screw, a stator sleeve, and a pressure stabilizing filter element. The single-head screw is properly sleeved in the stator sleeve. One end of the single-head screw is rotationally connected to the inner side wall of one end of the stator sleeve through the pressure stabilizing filter element. The other end of the single-head screw is provided with a moving valve seat. The outer diameter of the moving valve seat is greater than the outer diameter of the end face of the other end of the single-head screw. The inner side wall of the other end of the stator sleeve is connected to the radio frequency part. The radio frequency part has an axially penetrating radio frequency flow channel. A gap flow channel is formed between the single-head screw and the stator sleeve. The moving valve seat has a communication cavity and axially abuts against the radio frequency part. A first flow channel through hole communicating with the communication cavity is provided on the end face of the moving valve seat close to the radio frequency part. A second flow channel through hole communicating with the communication cavity is provided on the side wall of the moving valve seat;

[0006] When the single-headed screw rotates under the drive of the fluid in the clearance flow channel, the moving valve seat radially knocks on the stator sleeve, generating radial vibration, and causing the flow area of the RF flow channel to change periodically. Furthermore, the axial vibration part and the circumferential vibration part respectively perform axial vibration and circumferential vibration relative to the drill pipe connection part.

[0007] The beneficial effects of the present invention are as follows: The hydraulic oscillator of the present invention uses a single-headed screw and is connected to the moving valve seat. It can utilize the fluid to drive the single-headed screw to rotate in the stator sleeve, drive the moving valve seat to reciprocate up and down and knock on the stator sleeve to generate a radial vibration effect. Further, the axial vibration part is used to generate axial vibration, and the circumferential vibration part is used to generate circumferential vibration. Through the multi-dimensional vibration superposition and coupling, it can not only improve the oscillation effect of the hydraulic oscillator, but also more effectively change static friction into dynamic friction, reduce the friction coefficient between the drill string and the wellbore wall, effectively improve problems such as horizontal well sticking due to drag, reduce the frictional resistance torque, and increase the drill string extension limit of the ultra-long horizontal well.

[0008] On the basis of the above technical solution, the present invention can be further improved as follows.

[0009] Further, a fixed valve seat is provided at one end of the RF part close to the moving valve seat. The fixed valve seat includes a support seat, an eccentric seat, and a sheath. The sheath is sleeved on one end of the RF part close to the moving valve seat. The support seat is a hollow structure and is fixed on the end face of one end of the RF part through a fixing pin. The eccentric seat is fixed on the support seat and is hermetically connected in the sheath. An eccentric flow hole communicating with the RF flow channel is provided on the eccentric seat, and the eccentric flow hole is arranged upward deviating from the axis of the RF part. The first flow channel through hole is arranged eccentrically downward on the end face of one end of the moving valve seat.

[0010] The beneficial effect of adopting the above further solution is that by using the eccentrically arranged first flow channel through hole and eccentric flow hole, the moving valve seat can reciprocally radially knock on the stator sleeve, generating radial vibration while also causing the flow area of the RF flow channel to change periodically.

[0011] Further, when the single-headed screw rotates under the drive of the fluid in the clearance flow channel, the first flow channel through hole of the moving valve seat is axially corresponding to the eccentric flow hole or the moving valve seat blocks the eccentric flow hole.

[0012] Further, the stator sleeve includes a stator inner cylinder and a stator outer cylinder. The stator inner cylinder is fixedly sleeved in the stator outer cylinder. The single-headed screw is properly sleeved in the stator inner cylinder, and the other end of the single-headed screw extends out of the stator inner cylinder. The moving valve seat is located outside one end of the stator inner cylinder.

[0013] Further, the circumferential vibration part includes a threaded outer cylinder, and the drill pipe connection part includes a mandrel piston. One end of the threaded outer cylinder is hermetically connected to one end of the axial vibration part. The mandrel piston is sleeved in the threaded outer cylinder and is threadedly connected to the threaded outer cylinder in a matching manner. One end of the mandrel piston located inside the threaded outer cylinder is elastically connected to the axial vibration part.

[0014] Further, a nine - headed thread structure is provided on the inner side wall of the threaded outer cylinder.

[0015] Further, one end of the threaded outer cylinder is threadedly connected to the outer side wall of one end of the axial vibration part, and the inner side wall of the threaded outer cylinder and the inner side wall of the axial vibration part are also limited by anti - retreat steel balls.

[0016] Further, a sealing joint is hermetically connected to the other end of the threaded outer cylinder, and the mandrel piston passes through the sealing joint and is hermetically and rotationally connected to the sealing joint.

[0017] Further, the axial vibration part includes a disc spring outer cylinder. A disc spring is arranged inside the disc spring outer cylinder. One end of the disc spring outer cylinder is hermetically connected to the outer side wall of the stator sleeve, and the other end of the disc spring outer cylinder is hermetically connected to the threaded outer cylinder. The disc spring is sleeved on the mandrel piston. One end of the disc spring is fixed on the inner side wall of the disc spring outer cylinder, and the other end of the disc spring is connected to the outer side wall of the mandrel piston.

[0018] Further, a disc spring groove is provided on the inner side wall of the disc spring outer cylinder. A pressure cap is hermetically sleeved on the outer side wall of the mandrel piston, and the outer peripheral side wall of the pressure cap is hermetically and rotationally abutted against the disc spring groove; the other end of the disc spring abuts against the pressure cap. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 is the axial sectional structure schematic diagram of the hydraulic oscillator for three - dimensional multi - directional vibration in horizontal well drilling of the present invention;

[0020] Figure 2 is the sectional structure schematic diagram of the cooperation between the mandrel piston and the threaded outer cylinder of the present invention;

[0021] Figure 3 is the sectional structure schematic diagram of the cooperation between the middle part of the single - start screw and the stator sleeve of the present invention;

[0022] Figure 4 is the sectional structure schematic diagram of the cooperation between the end part of the single - start screw and the stator sleeve of the present invention;

[0023] Figure 5 is Figure 1 the enlarged structure schematic diagram of part A in

[0024] Figure 6 isFigure 1 Schematic diagram of the enlarged structure of part B;

[0025] Figure 7 is Figure 1 Schematic diagram of the enlarged structure of part C;

[0026] Figure 8 is Figure 1 Schematic diagram of the enlarged structure of part D;

[0027] Figure 9 The structural principle of the axial vibration of the hydraulic oscillator of the present invention Figure 1 ;

[0028] Figure 10 The structural principle of the axial vibration of the hydraulic oscillator of the present invention Figure 2 .

[0029] In the attached drawings, the list of components represented by each label is as follows:

[0030] 1. Drill pipe connection part; 11. Mandrel piston; 12. Threaded outer cylinder; 13. Nine-headed thread structure;

[0031] 2. Axial vibration part; 21. Disc spring; 22. Disc spring outer cylinder; 23. Disc spring groove; 24. Compression cap;

[0032] 3. Power part; 31. Single-headed screw; 32. Stator inner cylinder; 33. Pressure stabilizing filter element; 34. Moving valve seat; 35. Clearance flow channel; 36. First flow channel through hole; 37. Communication cavity; 38. Stator outer cylinder;

[0033] 4. Radio frequency part; 41. Fixed valve seat; 42. Eccentric flow hole; 43. Fixed pin; 44. Sheath; 45. Eccentric seat; 46. Support seat; 47. Eccentric ring;

[0034] 5. Anti-back steel ball; 6. Sealing joint; 7. Rotary sealing ring; 71. Wear-resistant band; 72. Dust-proof ring; 73. Plug; 74. O-ring;

[0035] 8. Connecting cylinder; 9. Radial vibration part; 10. Circumferential vibration part. Specific embodiments

[0036] The principles and features of the present invention will be described below with reference to the attached drawings. The examples given are only used to explain the present invention and are not intended to limit the scope of the present invention.

[0037] As Figures 1 to 10As shown in the figure, a hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling according to this embodiment includes a drill pipe connection part 1, a circumferential vibration part 10, an axial vibration part 2, a radial vibration part 9, a power part 3, and a radio frequency part 4 that are sequentially connected axially. The outer sidewall of the drill pipe connection part 1 is threadedly connected to the circumferential vibration part 10, and one end of the drill pipe connection part 1 is elastically connected to the axial vibration part 2; the power part 3 includes a single-head screw 31, a stator sleeve, and a pressure-stabilizing filter element 33. The radial vibration part 9 includes a moving valve seat 34. The single-head screw 31 is properly sleeved inside the stator sleeve. One end of the single-head screw 31 is rotatably connected to the inner sidewall of one end of the stator sleeve through the pressure-stabilizing filter element 33. The other end of the single-head screw 31 is provided with a moving valve seat 34. The outer diameter of the moving valve seat 34 is larger than the outer diameter of the end face of the other end of the single-head screw 31. The inner sidewall of the other end of the stator sleeve is connected to a radio frequency part 4. The radio frequency part 4 has an axially penetrating radio frequency flow channel. A clearance flow channel 35 is formed between the single-head screw 31 and the stator sleeve. The moving valve seat 34 has a communication cavity 37 and axially abuts against the radio frequency part 4. A first flow channel through hole 36 communicating with the communication cavity 37 is provided on the end face of the moving valve seat 34 close to the radio frequency part 4. A second flow channel through hole communicating with the communication cavity 37 is provided on the side wall of the moving valve seat 34;

[0038] Among them, when the single-head screw 31 rotates under the drive of the fluid in the clearance flow channel 35, the moving valve seat 34 radially knocks on the stator sleeve to generate radial vibration, and makes the flow area of the radio frequency flow channel change periodically, thereby enabling the axial vibration part and the circumferential vibration part to perform axial vibration and circumferential vibration relative to the drill pipe connection part respectively.

[0039] Specifically, one axial end of the axial vibration part 2 is connected to the stator sleeve, and the other axial end of the axial vibration part 2 is connected to one axial end of the circumferential vibration part 10.

[0040] Specifically, as Figures 8 to 10As shown in the figure, a fixed valve seat 41 is provided at one end of the radio frequency part 4 of this embodiment close to the moving valve seat 34. The fixed valve seat 41 includes a support seat 46, an eccentric seat 45 and a sheath 44. The sheath 44 is sleeved on one end of the radio frequency part 4 close to the moving valve seat 34. The support seat 46 is of a hollow structure and is fixed to one end face of the radio frequency part 4 through a fixing pin 43. The eccentric seat 45 is fixed on the support seat 46 and is hermetically connected inside the sheath 44. An eccentric flow hole 42 communicating with the radio frequency flow channel is provided on the eccentric seat 45, and the eccentric flow hole 42 is arranged upward deviating from the axis of the radio frequency part 4. The first flow channel through hole 36 is arranged eccentrically downward on one end face of the moving valve seat 34. By adopting the eccentrically arranged first flow channel through hole and eccentric flow hole, when the moving valve seat reciprocally radially knocks the stator sleeve, while generating radial vibration, the flow area of the radio frequency flow channel can also be periodically changed. The up and down directions in this embodiment are subject to the up and down display directions in the figure.

[0041] A preferred solution of this embodiment is that both the first flow channel through hole 36 and the eccentric flow hole 42 are circular holes, and the inner diameter of the first flow channel through hole 36 is the same as that of the eccentric flow hole 42.

[0042] Specifically, as Figure 8 shown, one end of the communication cavity 37 of the moving valve seat 34 is of an open structure, and an eccentric ring 47 is provided in the open structure, and the first flow channel through hole 36 is provided on the eccentric ring 47.

[0043] As Figure 9 and Figure 10 shown, when the single - head screw 31 of this embodiment rotates under the drive of the fluid in the clearance flow channel 35, the first flow channel through hole 36 of the moving valve seat 34 and the eccentric flow hole 42 are axially corresponding or the moving valve seat 34 blocks the eccentric flow hole 42.

[0044] As Figure 3 、 Figure 4 、 Figure 7 and Figure 8 shown, the stator sleeve of this embodiment includes a stator inner cylinder 32 and a stator outer cylinder 38. The stator inner cylinder 32 is fixedly sleeved inside the stator outer cylinder 38. The single - head screw 31 is suitably sleeved inside the stator inner cylinder 32. The other end of the single - head screw 31 extends out of the stator inner cylinder 32, and the moving valve seat 34 is located outside one end of the stator inner cylinder 32. Among them, the structure of the stator sleeve and the single - head screw 31 in this embodiment adopts the commonly used positive displacement motor in the prior art. The number of spiral heads of the single - head screw 31 of the positive displacement motor is 1 less than the number of spiral heads of the stator inner cylinder 32. As Figure 3As shown in the figure. The movable valve seat 34 is located outside one end of the stator inner cylinder 32. When the single - start screw 31 rotates within the stator inner cylinder 32, the movable valve seat 34 rotates and moves up and down along the inner side wall of the stator outer cylinder 38 while knocking on the inner side wall of the stator outer cylinder 38.

[0045] As Figure 2 and Figure 5 As shown in the figure, the circumferential vibration part 10 of this embodiment includes a threaded outer cylinder 12. The drill pipe connection part 1 includes a mandrel piston 11. One end of the threaded outer cylinder 12 is hermetically connected to one end of the axial vibration part 2. The mandrel piston 11 is sleeved within the threaded outer cylinder 12 and is threadedly connected to the threaded outer cylinder 12 in a matching manner. One end of the mandrel piston 11 located within the threaded outer cylinder 12 is elastically connected to the axial vibration part 2.

[0046] As Figure 2 Preferably, as shown in the figure, a nine - head thread structure 13 is provided on the inner side wall of the threaded outer cylinder 12.

[0047] As Figure 5 As shown in the figure, one end of the threaded outer cylinder 12 of this embodiment is threadedly connected to the outer side wall of one end of the axial vibration part 2, and the inner side wall of the threaded outer cylinder 12 and the inner side wall of the axial vibration part 2 are also limited by anti - backing steel balls 5.

[0048] As Figure 5 As shown in the figure, a sealing joint 6 is hermetically connected to the other end of the threaded outer cylinder 12 of this embodiment. The mandrel piston 11 passes through the sealing joint 6 and is hermetically and rotationally connected to the sealing joint 6.

[0049] As Figure 6 As shown in the figure, the axial vibration part 2 of this embodiment includes a disc spring outer cylinder 22. A disc spring 21 is provided within the disc spring outer cylinder 22. One end of the disc spring outer cylinder 22 is hermetically connected to the outer side wall of the stator sleeve. The other end of the disc spring outer cylinder 22 is hermetically connected to the threaded outer cylinder 12. The disc spring 21 is sleeved on the mandrel piston 11. One end of the disc spring 21 is fixed on the inner side wall of the disc spring outer cylinder 22, and the other end of the disc spring 21 is connected to the outer side wall of the mandrel piston 11.

[0050] As Figure 6 As shown in the figure, a disc spring groove 23 is provided on the inner side wall of the disc spring outer cylinder 22 of this embodiment. A pressure cap 24 is hermetically sleeved on the outer side wall of the mandrel piston 11. The outer peripheral side wall of the pressure cap 24 is hermetically and rotationally abutted against the disc spring groove 23. The other end of the disc spring 21 abuts against the pressure cap 24. Among them, the outer side wall of the pressure cap 24 is hermetically and rotationally connected to the inner side wall of the disc spring outer cylinder 22 through a wear - resistant band 71 and a rotary seal ring 7, and the inner side wall of the pressure cap 24 is hermetically connected to the outer side wall of the mandrel piston 11 through an O - ring.

[0051] Specifically, as Figure 5 shown, both ends of the threaded outer cylinder 12 of this embodiment are hermetically and limit-connected to the outer side wall of the disc spring outer cylinder 22 and the outer side wall of the sealing joint 6 through anti-retreat steel balls 5 and plug heads 73. The inner side wall of the sealing joint 6 is hermetically and rotationally connected to the outer side wall of the mandrel piston 11 through a rotary seal ring 7, a wear-resistant band 71, and a dust-proof ring 72.

[0052] Specifically, as Figure 7 shown, one end of the stator outer cylinder 38 of this embodiment is connected to the disc spring outer cylinder 22 through a connecting cylinder 8. Both ends of the connecting cylinder 8 are respectively inserted into the stator outer cylinder 38 and the disc spring outer cylinder 22 and are respectively connected and limited to the stator outer cylinder 38 and the disc spring outer cylinder 22 through anti-retreat steel balls 5 and plug heads 73. Moreover, both ends of the connecting cylinder 8 are also hermetically connected to the stator outer cylinder 38 and the disc spring outer cylinder 22 respectively through O-ring 74. Figure 7 In, a pressure stabilizing filter element 33 is further provided at one end of the single-headed screw 31. The pressure stabilizing filter element 33 can be arranged on the inner side wall of the stator outer cylinder 38 or the inner side wall of the connecting cylinder 8 for filtering fluid and stabilizing pressure. A gap is reserved between the pressure stabilizing filter element 33 and the end of the mandrel piston 11. The connecting cylinder 8 can also limit the axial movement of the mandrel piston 11. Specifically, one end of the compression cap 24 can be abutted and limited to the end of the connecting cylinder 8 to prevent excessive axial movement of the mandrel piston 11.

[0053] For the hydraulic oscillator of this embodiment, aiming at the actual application working conditions, the drill pipe connection part (i.e., the mandrel piston) can be regarded as one part, and all other components can be regarded as another part. In the actual application working conditions, the mandrel piston is connected to the drill pipe and the mandrel piston does not move. Then all other components will perform three-dimensional multi-directional movements relative to the mandrel piston. And the axial vibration part and the circumferential vibration part are connected together. In fact, the axial vibration part and the circumferential vibration part perform axial vibration and circumferential vibration simultaneously. Except for the axial vibration part and the circumferential vibration part, based on the connection relationship of all other components, all other components perform axial vibration and circumferential vibration relative to the mandrel piston, that is, the radial vibration part, the power part, and the RF part also perform axial vibration and circumferential vibration relative to the mandrel piston. At the same time, the radial vibration part also needs to radially strike the stator sleeve. In this way, the entire hydraulic oscillator except the mandrel piston performs axial vibration, circumferential vibration, and radial vibration.

[0054] To facilitate the description of three-dimensional vibration, the principle of the hydraulic oscillator is described separately by detaching from the actual working conditions. The fluid enters the power part through the inner cavity flow channel of the hydraulic oscillator, driving the single-headed screw of the power part to rotate. The single-headed screw, as a rotor, drives the moving valve seat to reciprocate up and down, as Figure 4As shown, the outer cylinder of the stator is struck to generate a radial vibration effect. The reciprocating motion of the moving valve seat causes the flow area between the moving valve seat and the fixed valve seat to change periodically, thereby generating a radio frequency effect, resulting in a periodically changing pulse pressure near the axial vibration part. Under the action of the pulse pressure, the mandrel piston makes an axial periodic reciprocating motion. At the same time, due to the threaded connection between the mandrel piston and the threaded outer cylinder, the mandrel piston also makes a circumferential rotational motion, generating a circumferential vibration effect; in actual working conditions, the mandrel piston is fixed, and other components connected to it vibrate axially and circumferentially relatively. Figure 9 In [a certain situation], the moving valve seat blocks the eccentric flow hole on the fixed valve seat. The mandrel piston moves axially under the pulse pressure and rotates circumferentially clockwise under the limitation of the threaded outer cylinder; in actual working conditions, the mandrel piston is fixed, and the threaded outer cylinder rotates circumferentially clockwise. Figure 10 In [a certain situation], the first flow channel through hole of the moving valve seat corresponds to the eccentric flow hole on the fixed valve seat. The mandrel piston returns under the action of the disc spring and rotates circumferentially counterclockwise under the limitation of the threaded outer cylinder; in actual working conditions, the mandrel piston does not move, and the threaded outer cylinder rotates circumferentially counterclockwise.

[0055] The hydraulic oscillator of this embodiment uses a single-start screw and connects the moving valve seat. It can use the fluid to drive the single-start screw to rotate in the stator sleeve, drive the moving valve seat to move up and down reciprocally and strike the stator sleeve to generate a radial vibration effect. Further, it uses the axial vibration part to generate axial vibration and the circumferential vibration part to generate circumferential vibration. Through the multi-dimensional vibration superposition and coupling, it can not only improve the oscillation effect of the hydraulic oscillator, but also more effectively change static friction to dynamic friction, reduce the friction coefficient between the drill string and the wellbore wall, effectively improve problems such as horizontal well sticking due to pack-off, reduce the frictional resistance torque, and increase the extension limit of the drill string in ultra-long horizontal wells. The hydraulic oscillator of this embodiment solves the limitation of the traditional hydraulic oscillator that only relies on water pulse energy to generate a single vibration mode from a higher vibration dimension, and effectively solves the problem of reducing frictional resistance during horizontal well drilling.

[0056] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present invention.

[0057] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0058] In the present invention, unless otherwise clearly specified and defined, terms such as "mounted", "connected", "coupled", "fixed", etc. shall be construed in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the internal communication of two components or the interaction relationship between two components, unless otherwise clearly defined. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0059] In the present invention, unless otherwise clearly specified and defined, the first feature being "on" or "under" the second feature may be that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, the first feature being "above", "over" and "on top of" the second feature may be that the first feature is directly above or obliquely above the second feature, or merely indicates that the first feature has a higher horizontal height than the second feature. The first feature being "under", "beneath" and "underneath" the second feature may be that the first feature is directly below or obliquely below the second feature, or merely indicates that the first feature has a lower horizontal height than the second feature.

[0060] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "example", "specific example", or "some examples", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples. In addition, without contradiction, those skilled in the art can combine and combine the different embodiments or examples described in this specification and the features of different embodiments or examples.

[0061] Although the embodiments of the present invention have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention.

Claims

1. A hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling, characterized in that It includes a drill pipe connection part, a circumferential vibration part, an axial vibration part, a radial vibration part, a power part, and a radio frequency part that are connected in sequence along the axis. The outer side wall of the drill pipe connection part is threadedly connected to the circumferential vibration part, and one end of the drill pipe connection part is elastically connected to the axial vibration part; The radial vibration part includes a moving valve seat. The power part includes a single-headed screw, a stator sleeve, and a voltage stabilizing filter element. The single-headed screw is appropriately sleeved inside the stator sleeve. One end of the single-headed screw is rotationally connected to the inner side wall of one end of the stator sleeve through the voltage stabilizing filter element. The other end of the single-headed screw is provided with a moving valve seat. The outer diameter of the moving valve seat is greater than the outer diameter of the end face of the other end of the single-headed screw. The inner side wall of the other end of the stator sleeve is connected with a radio frequency part. The radio frequency part has an axially penetrating radio frequency flow channel. A gap flow channel is formed between the single-headed screw and the stator sleeve. The moving valve seat has a communication cavity and axially abuts against the radio frequency part. A first flow channel through hole communicating with the communication cavity is provided on the end face of one end of the moving valve seat close to the radio frequency part. A second flow channel through hole communicating with the communication cavity is provided on the side wall of the moving valve seat; Wherein, when the single-headed screw rotates under the drive of the fluid in the gap flow channel, the moving valve seat radially knocks on the stator sleeve to generate radial vibration, and makes the flow area of the radio frequency flow channel change periodically, so that the axial vibration part and the circumferential vibration part respectively perform axial vibration and circumferential vibration relative to the drill pipe connection part; A fixed valve seat is provided at one end of the radio frequency part close to the moving valve seat. The fixed valve seat includes a support seat, an eccentric seat, and a sheath. The sheath is sleeved on one end of the radio frequency part close to the moving valve seat. The support seat is a hollow structure and is fixed on the end face of one end of the radio frequency part through a fixing pin. The eccentric seat is fixed on the support seat and is hermetically connected inside the sheath; an eccentric flow hole communicating with the radio frequency flow channel is provided on the eccentric seat, and the eccentric flow hole is arranged upward deviating from the axis of the radio frequency part; the first flow channel through hole is arranged eccentrically downward on the end face of one end of the moving valve seat; When the single-headed screw rotates under the drive of the fluid in the gap flow channel, the first flow channel through hole of the moving valve seat is axially correspondingly arranged with the eccentric flow hole or the moving valve seat blocks the eccentric flow hole.

2. The hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling according to claim 1, characterized in that The stator sleeve includes a stator inner cylinder and a stator outer cylinder. The stator inner cylinder is fixedly sleeved inside the stator outer cylinder. The single-headed screw is appropriately sleeved inside the stator inner cylinder. The other end of the single-headed screw extends out of the stator inner cylinder, and the moving valve seat is located outside one end of the stator inner cylinder.

3. The hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling according to claim 1, wherein The circumferential vibration part includes a threaded outer cylinder. The drill pipe connection part includes a mandrel piston. One end of the threaded outer cylinder is hermetically connected to one end of the axial vibration part. The mandrel piston is sleeved inside the threaded outer cylinder and is threadedly connected to the threaded outer cylinder in a matching manner. One end of the mandrel piston located inside the threaded outer cylinder is elastically connected to the axial vibration part.

4. The hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling according to claim 3, wherein, A nine-headed thread structure is provided on the inner side wall of the threaded outer cylinder.

5. The hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling according to claim 3, characterized in that One end of the threaded outer cylinder is threadedly connected to the outer side wall of one end of the axial vibration part, and a retaining steel ball is also used for limiting between the inner side wall of the threaded outer cylinder and the inner side wall of the axial vibration part.

6. The hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling according to claim 3, wherein, A sealing joint is hermetically connected to the other end of the threaded outer cylinder, and the mandrel piston passes through the sealing joint and is hermetically and rotationally connected to the sealing joint.

7. The hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling according to any one of claims 3 to 6, characterized in that, The axial vibration part includes a disc spring outer cylinder, a disc spring is arranged in the disc spring outer cylinder, one end of the disc spring outer cylinder is hermetically connected to the outer side wall of the stator sleeve, the other end of the disc spring outer cylinder is hermetically connected to the threaded outer cylinder, the disc spring is sleeved on the mandrel piston, one end of the disc spring is fixed to the inner side wall of the disc spring outer cylinder, and the other end of the disc spring is connected to the outer side wall of the mandrel piston.

8. The hydraulic oscillator for three-dimensional multi-directional vibration in horizontal well drilling according to claim 7, characterized in that, A disc spring groove is arranged on the inner side wall of the disc spring outer cylinder, a compression cap is hermetically sleeved on the outer side wall of the mandrel piston, and the outer peripheral side wall of the compression cap is hermetically and rotationally abutted against the disc spring groove; the other end of the disc spring abuts against the compression cap.

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