Variable-amplitude hydraulic oscillator

Abstract

The invention relates to a variable-amplitude hydraulic oscillator, and belongs to the technical field of petroleum and natural gas well drilling matching tools. The tool aims at solving the problems that a traditional hydraulic oscillator is single in vibration mode, and equipment is prone to damage and low in efficiency due to the fact that the amplitude cannot be adjusted. The device structurally comprises a flow conversion short section, an axial vibration short section, a power short section and a radial vibration short section which are connected in sequence. The flow conversion short section achieves switching of a high amplitude mode, a low amplitude mode and a closing mode through the synergistic effect of a hole-shaped piston, a ratchet wheel and a flow channel conversion mandrel and by means of interruption and recovery of fluid flowing. The axial vibration short section adopts a two-stage piston structure to generate efficient axial vibration, the power short section is matched with a dynamic valve plate and a static valve plate through a screw rotor to generate high-frequency pressure pulses, and the radial vibration short section forms transverse vibration by means of centrifugal movement of a pendulum ball. By adjusting the fluid path, the tool can output shock waves of different amplitudes, friction between a drilling tool and the well wall is reduced, and meanwhile fluid pressure is maintained in a closed mode so that clamping stagnation of a pipe column can be avoided. The invention has the beneficial effects of prolonging the service life of equipment, improving the drilling efficiency, reducing the risk of jamming of the drilling tool and adapting to complex formation conditions.

Description

Technical Field

[0001] The invention relates to the technical field of supporting tools for oil and natural gas drilling, in particular to a variable amplitude hydraulic oscillator. Background Art

[0002] In the field of oil and gas drilling, with the widespread application of complex wells such as extended reach wells and long horizontal wells, the friction problem between the drill string and the well wall has become increasingly prominent. In the traditional solution, adding a mud motor as a component of the lower drilling tool assembly can assist in propulsion by rotating the drill bit, but when a more flexible continuous tubing is used to replace the rigid drill pipe, the continuous tubing is prone to aggravating the friction problem due to bending and deformation. Therefore, the prior art introduces a hydraulic oscillation tool to reduce the friction coefficient between the pipe string and the well wall by continuously generating shock waves, thereby pushing the pipe string to drill to the bottom of the well. The hydraulic oscillator can effectively reduce friction and improve the drilling pressure transmission efficiency by converting static friction into dynamic friction.

[0003] Traditional hydraulic oscillation tools have significant defects in operation: the large amplitude pressure pulses and high-frequency vibrations they generate can cause fatigue damage to the lower drilling tool assembly, wellbore tubulars, and even ground equipment, shortening the service life of the equipment. The vibration mode of existing tools is single and cannot be adjusted. During operation, the tool needs to be frequently started and stopped to balance friction control and equipment loss, which significantly increases non-productive time, not only reducing operation efficiency, but also leading to additional energy waste. For example, frequent start-stop operations require the drilling rig power system to repeatedly load high loads, resulting in increased fuel consumption. Frequent replacement of parts due to equipment fragility further increases material consumption and carbon emissions during manufacturing and transportation. In addition, the "off" mode of existing vibration tools cannot maintain fluid pressure, which can easily cause tubular string jamming during the vibration stop period. For rigid drill pipes, they need to be disassembled section by section to adjust the position. Although the continuous tubing can be recovered by reeling, its long-distance tripping operation is still time-consuming and costly. Therefore, there is an urgent need for a multi-mode tool that can dynamically adjust vibration parameters (such as amplitude and frequency) and support continuous transmission of high-pressure fluids to break the contradiction between efficiency and reliability in existing technologies and reduce the energy intensity and carbon emissions of drilling operations.

[0004] In response to the above technical bottlenecks, the present invention aims to provide a variable amplitude hydraulic oscillator, which can realize switchable operation of high amplitude, low amplitude and closed mode by controlling the flow of pressurized fluid. The tool can output shock waves sufficient to overcome downhole resistance in "high amplitude mode", reduce equipment loss in "low amplitude mode", and maintain high-pressure fluid transmission in "closed mode" to avoid pipe string jamming. By optimizing vibration mode and energy efficiency management, the horizontal well operation efficiency and equipment service life are significantly improved, providing innovative solutions for green and low-carbon drilling. Summary of the invention

[0005] In order to achieve the above-mentioned object of the invention, the technical solution adopted by the present invention is as follows:

[0006] A variable amplitude hydraulic oscillator, comprising: a flow conversion nipple, an axial vibration nipple, a power nipple, and a radial vibration nipple, wherein the flow conversion nipple, the axial vibration nipple, the power nipple, and the radial vibration nipple are sequentially connected by pipe thread sealing;

[0007] The flow conversion nipple comprises an upper joint of the flow conversion nipple, a lower joint of the flow conversion nipple, a flow stabilizing assembly, a piston assembly, and a flow conversion assembly. The flow stabilizing assembly is threadedly connected to the upper joint of the flow conversion nipple, the piston assembly is fixed to the upper end of the lower joint of the flow conversion nipple, and the flow conversion assembly is threadedly connected to the lower joint of the flow conversion nipple;

[0008] The flow stabilizing assembly includes a spiral flow stabilizing block, a guide block, a tubular cup, and a centering device. The spiral flow stabilizing block is installed inside the upper joint of the flow conversion short joint. The guide block is concentrically connected to the tubular cup through a thread. The tubular cup is threadedly connected to the centering device. The centering device is threadedly connected to the upper joint of the flow conversion short joint.

[0009] The piston assembly includes a piston stabilizing rod, a hole-shaped piston, an upper ratchet, a lower ratchet, a ratchet sleeve, a seal, and a spring. The piston stabilizing rod is threadedly connected to the hole-shaped piston and passes through the center hole of the centering device. The hole-shaped piston is installed in the upper ratchet and the lower ratchet. The upper ratchet and the lower ratchet are installed in the ratchet sleeve in a coordinated manner. The ratchet sleeve is axially fixed through the lower end face of the upper joint of the flow conversion short section and the upper end face of the flow channel conversion spindle. The spring is installed between the hole-shaped piston and the flow channel conversion spindle.

[0010] The flow conversion assembly includes a flow channel conversion spindle, an outlet base, an outlet spring, and an outlet valve plate. The flow channel conversion spindle is installed inside the lower joint of the flow conversion nipple and is axially positioned through an internal protrusion. The outlet base is threadedly connected to the lower end of the flow channel conversion spindle. The outlet spring is installed between the outlet base and the outlet valve plate.

[0011] The axial vibration pup joint includes a transmission spindle, a sliding outer sleeve, an upper joint of the axial vibration pup joint, a disc spring, a wear-resistant bushing, a piston shaft, a first piston, a second piston, and a lower joint of the axial vibration pup joint. The transmission spindle is threadedly connected with the lower joint of the flow conversion pup joint. The sliding outer sleeve, the upper joint of the axial vibration pup joint, the wear-resistant bushing, and the lower joint of the axial vibration pup joint are threadedly connected in sequence. The disc spring is installed on the transmission spindle, the piston shaft is threadedly connected with the transmission spindle, and the first piston and the second piston are installed outside the piston shaft.

[0012] The power sub comprises a first joint, an upper joint of the power sub, a screw sleeve, a screw rotor, a rotor joint, a moving valve plate, and a static valve plate. The upper joint of the power sub is threadedly connected to the first joint, the screw sleeve is threadedly connected to the upper joint of the power sub, the screw rotor is located in the spiral cavity of the screw sleeve, the lower end of the screw rotor is connected to the moving valve plate through the rotor joint, and the static valve plate is fixedly connected to the screw sleeve;

[0013] The radial vibration pup joint comprises a second joint, a radial vibration pup joint housing, a swing ball seat, and a swing ball. The second joint is threadedly connected to the screw sleeve, the radial vibration pup joint housing is threadedly connected to the second joint, the swing ball seat is installed inside the radial vibration pup joint housing, and the swing ball is installed in the swing ball seat.

[0014] Furthermore, the guide block has a wedge-shaped flow channel, which can reduce the fluctuation of the flow at the inlet and achieve a stabilizing flow effect.

[0015] Furthermore, the porous piston has three pairs of relative flow channels, and the flow channel conversion spindle has three pairs of relative leakage channels, each pair of relative leakage channels has an inlet and an outlet, and the outlet of each pair of relative flow channels of the porous piston is aligned with the inlet of each pair of relative leakage channels of the flow channel conversion spindle and extends to the outlet of the leakage channel.

[0016] Furthermore, a pair of upper and lower ratchet wheels that cooperate with each other are installed in the ratchet sleeve, and the upper and lower ratchet wheels are rotationally fixed to the ratchet sleeve by a sliding key. The hole-shaped piston can move axially relative to the upper ratchet wheel, the lower ratchet wheel and the ratchet sleeve. The upper ratchet wheel and the lower ratchet wheel both have a relative irregular edge surface with peaks and troughs, and the hole-shaped piston has a protrusion on its circumference, which extends to the outer surface of the upper and lower ratchet wheels. The axial force on the hole-shaped piston will cause it to rotate relative to the ratchet wheel, which is beneficial to ensure accurate switching and stability of different flow modes.

[0017] Furthermore, the outlets of the three pairs of flow channels of the hole-shaped piston are all provided with internal threads, and the outlets of the second pair of flow channels and the third pair of flow channels are respectively screwed into a pair of the seals for sealing, and the four seals are all composed of screws, and the screws are provided with an annular sealing rubber ring which tightly covers part of the thread of the screw head, and once the seals are screwed into their respective outlets, both pairs of flow channels (i.e., the second pair and the third pair) will be blocked.

[0018] Furthermore, the flow channel conversion spindle includes three pairs of jet channels, the first pair of leakage channels have two outlets, part of the fluid flows out of the tool through the leakage port, and part of the fluid enters the lower part of the tool through the lower end outlet, the second pair of leakage channel outlets are located inside the tool, all the fluid flows into the lower part of the tool, and the third pair of leakage channel outlets are aligned with the tool leakage outlet, and all the fluid flows out of the tool.

[0019] Furthermore, the end of the flow channel conversion spindle has an outlet valve plate connected to the outlet spring. When the fluid pressure exceeds a preset threshold and is sufficient to push open the outlet valve plate, the outlet valve plate allows the fluid to flow downward into the lower part of the tool.

[0020] Furthermore, the axial vibration short section includes the first piston and the second piston, and a pressure chamber is formed by the gap between the piston and the shell. Fluid pressure changes drive the piston to reciprocate, and the double-stage piston is beneficial to improving the effect of axial vibration.

[0021] Furthermore, a liquid inlet chamber is provided on the upper end surface of the movable valve plate, a plurality of liquid inlet holes arranged at equal angles are provided on the peripheral wall of the liquid inlet chamber, an eccentric hole is provided on the movable valve plate, and a flow hole is provided in the static valve plate. The movable valve plate moves eccentrically, so that the eccentric hole of the movable valve plate and the flow hole of the static valve plate are periodically misaligned, thereby generating high-frequency pressure pulses.

[0022] Furthermore, the pendulum ball seat is provided with radial holes, a pendulum ball is provided in the pendulum ball seat, and the pendulum ball can move radially in the pendulum ball seat. The fluid drives the pendulum ball to move centrifugally, and the inertia of the pendulum ball impacts the inner wall of the pendulum ball seat to form periodic radial vibration.

[0023] The beneficial effects of the present invention are:

[0024] The variable amplitude function enables it to accurately adjust the amplitude according to the hardness and characteristics of rocks in different formations, adapting to various complex formation conditions, thereby more effectively crushing rocks and speeding up drilling.

[0025] Variable amplitude can prevent the lower drilling tool assembly, wellbore tubing and even ground equipment from operating continuously at a high amplitude, reduce fatigue damage to related equipment and increase equipment service life.

[0026] By adjusting the amplitude in real time and realizing multi-dimensional vibration output, it is possible to respond to complex situations underground more flexibly, so that the drill bit always maintains a good working condition during the drilling process, reduces the drilling and drilling operations caused by drill bit wear, drill sticking, etc., and improves the overall drilling efficiency.

[0027] The axial vibration adopts a two-stage piston structure, which can generate efficient vibration, effectively reduce the friction and torque between the drill bit and the well wall, reduce the friction and torque during drilling, prevent the drill bit from being supported, and thus increase the mechanical drilling speed.

[0028] The tool has axial and lateral multi-dimensional vibrations, which can make the drilling process more stable and smoother than single-direction vibrations, reduce the risk of drill bit sticking and drill tool damage, and avoid the phenomenon of drill bit "embedding".

[0029] The tool can accurately match the formation characteristics, avoid energy waste caused by ineffective vibration, improve overall energy efficiency, extend the service life of the equipment, reduce material consumption caused by frequent replacement of parts and carbon emissions in the manufacturing process, and reduce additional energy consumption for mud circulation and power maintenance during drilling operations. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings required for describing the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other accompanying drawings can be obtained based on these accompanying drawings without paying creative work.

[0031] Figure 1 It is a schematic diagram of the overall structure of the present invention;

[0032] Figure 2 It is a cross-sectional schematic diagram of the flow conversion short section of the present invention;

[0033] Figure 3 It is a cross-sectional schematic diagram of the axial vibration short section of the present invention;

[0034] Figure 4 It is a cross-sectional schematic diagram of the power sub of the present invention;

[0035] Figure 5 It is a cross-sectional schematic diagram of a radial vibration short section of the present invention;

[0036] Figure 6 It is a schematic diagram of the explosion of a part of the piston assembly of the present invention;

[0037] Figure 7 This is a schematic diagram of the flow channel conversion mandrel of the present invention;

[0038] FIG8 is a schematic diagram of the positional relationship between the hole-shaped piston guide pin and the ratchet wheel of the present invention;

[0039] Fig. 9 It is a cross-sectional schematic diagram of the flow conversion short section of the "high amplitude" mode of the present invention;

[0040] Fig.10 This is a cross-sectional schematic diagram of the flow conversion short section in the "off" mode of the present invention;

[0041] In the accompanying drawings, the components represented by the reference numerals are listed as follows:

[0042] 100-flow conversion nipple; 101-flow conversion nipple upper joint; 102-flow conversion nipple lower joint; 103-spiral flow stabilizing block; 104-tubular cup; 105-flow guide block; 106-piston stabilizing rod; 107-centering device; 108-hole piston; 109-ratchet sleeve; 110-upper ratchet; 111-lower ratchet; 112-seal; 113-spring; 114-flow channel conversion mandrel; 115-outlet base; 116-outlet spring; 117-outlet valve plate; 118-guide pin; 119-first drain port; 120-second drain port; 121-third drain port; 200-axial vibration nipple; 201-transmission spindle; 202-sliding jacket; 203-axial vibration short section upper joint; 204-disc spring; 205-wear-resistant bushing; 206-piston shaft; 207-first piston; 208-second piston; 209-axial vibration short section lower joint; 300-power short section; 301-first joint; 302-power short section upper joint; 303-screw sleeve; 304-screw rotor; 305-rotor joint; 306-piston stabilizing rod; 307-moving valve plate; 308-static valve plate; 400-radial vibration short section; 401-second joint; 402-radial vibration short section housing; 403-swing ball seat; 404-swing ball; DETAILED DESCRIPTION

[0043] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Generally, the components of the embodiments of the present invention described and shown in the drawings here can be arranged and designed in various different configurations.

[0044] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the invention claimed for protection, but merely represents selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0045] It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once an item is defined in one drawing, it does not need to be further defined and explained in the subsequent drawings. In addition, the terms "first", "second", etc. are only used to distinguish the description and cannot be understood as indicating or implying relative importance.

[0046] In addition, the technical features involved in the different embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other.

[0047] Embodiment 1

[0048] like Figure 1 As shown, this embodiment provides a variable amplitude hydraulic oscillator, comprising: a flow conversion subsection 100, an axial vibration subsection 200, a power subsection 300, and a radial vibration subsection 400, wherein the flow conversion subsection 100, the axial vibration subsection 200, the power subsection 300, and the radial vibration subsection 400 are sequentially connected by pipe thread sealing;

[0049] like Figure 2 As shown, the flow conversion nipple 100 includes an upper joint 101 of the flow conversion nipple, a lower joint 102 of the flow conversion nipple, a flow stabilizing assembly, a piston assembly, and a flow conversion assembly. The flow stabilizing assembly is threadedly connected to the upper joint 101 of the flow conversion nipple, the piston assembly is fixed to the upper end of the lower joint 102 of the flow conversion nipple, and the flow conversion assembly is threadedly connected to the lower joint 102 of the flow conversion nipple;

[0050] The flow stabilizing assembly includes a spiral flow stabilizing block 103, a guide block 105, a tubular cup 104, and a centering device 107. The spiral flow stabilizing block 103 is installed inside the upper joint 101 of the flow conversion short joint. The guide block 105 is concentrically connected to the tubular cup 104 through a thread. The tubular cup 104 is threadedly connected to the centering device 107. The centering device 107 is threadedly connected to the upper joint 101 of the flow conversion short joint.

[0051] The piston assembly includes a piston stabilizing rod 106, a hole-shaped piston 108, an upper ratchet 110, a lower ratchet 111, a ratchet sleeve 109, a seal 112, and a spring 113. The piston stabilizing rod 106 is threadedly connected to the hole-shaped piston 108 and passes through the center hole of the centering device 107. The hole-shaped piston 108 is installed in the upper ratchet 110 and the lower ratchet 111. The upper ratchet 110 and the lower ratchet 111 are installed in the ratchet sleeve 109 in a matching manner. The ratchet sleeve 109 is axially fixed through the lower end surface of the upper joint 101 of the flow conversion short section and the upper end surface of the flow channel conversion spindle 114. The spring 113 is installed between the hole-shaped piston 108 and the flow channel conversion spindle 114.

[0052] The flow conversion assembly includes a flow channel conversion spindle 114, an outlet base 115, an outlet spring 116, and an outlet valve plate 117. The flow channel conversion spindle 114 is installed inside the flow conversion nipple lower joint 102 and is axially positioned through an internal protrusion. The outlet base 115 is threadedly connected to the lower end of the flow channel conversion spindle 114. The outlet spring 116 is installed between the outlet base 115 and the outlet valve plate 117.

[0053] like Figure 3As shown, the axial vibration pup joint 200 includes a transmission spindle 201, a sliding sleeve 202, an axial vibration pup joint upper joint 203, a disc spring 204, a wear-resistant bushing 205, a piston shaft 206, a first piston 207, a second piston 208, and an axial vibration pup joint lower joint 209. The transmission spindle 201 is threadedly connected with the flow conversion pup joint lower joint 102, the sliding sleeve 202, the axial vibration pup joint upper joint 203, the wear-resistant bushing 205, and the axial vibration pup joint lower joint 209 are sequentially threadedly connected, the disc spring 204 is installed on the transmission spindle 201, the piston shaft 206 is threadedly connected with the transmission spindle 201, and the first piston 207 and the second piston 208 are installed outside the piston shaft 206;

[0054] like Figure 4 As shown, the power sub 300 includes a first joint 301, an upper joint 302 of the power sub, a screw sleeve 303, a screw rotor 304, a rotor joint 305, a movable valve plate 307, and a static valve plate 308. The upper joint 302 of the power sub is threadedly connected to the first joint 301, the screw sleeve 303 is threadedly connected to the upper joint 302 of the power sub, the screw rotor 304 is located in the spiral cavity of the screw sleeve 303, the lower end of the screw rotor 304 is connected to the movable valve plate 307 through the rotor joint 305, and the static valve plate 308 is fixedly connected to the screw sleeve 303;

[0055] like Figure 5 As shown, the radial vibration pup joint 400 includes a second joint 401, a radial vibration pup joint housing 402, a swing ball seat 403, and a swing ball 404. The second joint 401 is threadedly connected to the screw sleeve 303, the radial vibration pup joint housing 402 is threadedly connected to the second joint 401, the swing ball seat 403 is installed inside the radial vibration pup joint housing 402, and the swing ball 404 is installed in the swing ball seat 403.

[0056] The guide block 105 has a wedge-shaped flow channel, which can reduce the fluctuation of the flow at the inlet and achieve a stabilizing effect.

[0057] The porous piston 108 has three pairs of opposite flow channels, and the flow channel conversion spindle 114 has three pairs of opposite leakage channels, each pair of opposite leakage channels has an inlet and an outlet, and the outlet of each pair of opposite flow channels of the porous piston 108 is aligned with the inlet of each pair of opposite leakage channels of the flow channel conversion spindle 114 and extends to the leakage channel outlet.

[0058] A pair of mutually cooperating upper ratchet 110 and lower ratchet 111 are installed in the ratchet sleeve 109, and the upper ratchet 110 and the lower ratchet 111 are rotationally fixed to the ratchet sleeve 109 by a sliding key. The hole-shaped piston 108 can move axially relative to the upper ratchet 110, the lower ratchet 111 and the ratchet sleeve 109. The upper ratchet 110 and the lower ratchet 111 have a relative irregular edge surface with peaks and troughs. The hole-shaped piston 108 has a protrusion on its circumference, and the protrusion extends to the outer surface of the upper ratchet 110 and the lower ratchet 111. The axial force on the hole-shaped piston 108 will cause it to rotate relative to the ratchet, which is beneficial to ensure accurate switching and stability of different flow modes.

[0059] The outlets of the three pairs of flow channels of the porous piston 108 are all provided with internal threads, and the outlets of the second pair of flow channels and the third pair of flow channels are respectively screwed into a pair of the sealing members 112 for sealing, and the four sealing members 112 are all composed of screws, and the screws are provided with an annular sealing rubber ring which tightly covers part of the thread of the screw head. Once the sealing members 112 are screwed into their respective outlets, both pairs of flow channels will be blocked.

[0060] The flow channel conversion spindle 114 includes three pairs of leakage channels. The first pair of leakage channels has two outlets. Part of the fluid flows out of the tool through the leakage outlet, and part of the fluid enters the lower part of the tool through the lower end outlet. The second pair of jet channel outlets are located inside the tool, and all the fluid flows into the lower part of the tool. The third pair of jet channel outlets are aligned with the leakage outlets, and all the fluid flows out of the tool.

[0061] The end of the flow channel conversion spindle 114 has an outlet valve plate 117 connected to the outlet spring 116. When the fluid pressure exceeds a preset threshold and is sufficient to push open the outlet valve plate 117, the outlet valve plate 117 allows the fluid to flow downward into the lower part of the tool.

[0062] The first piston 207 and the second piston 208 are arranged in the axial vibration subsection 200. A pressure chamber is formed by the gap between the piston and the housing. Fluid pressure changes drive the piston to reciprocate. The double-stage piston is beneficial to improving the effect of axial vibration.

[0063] The upper end surface of the movable valve plate 307 is provided with a liquid inlet chamber, and the peripheral wall of the liquid inlet chamber is provided with a plurality of liquid inlet holes 306 arranged at equal angles. The movable valve plate 307 is provided with an eccentric hole, and the static valve plate 308 is provided with a flow hole. The movable valve plate 307 moves eccentrically, so that the eccentric hole of the movable valve plate 307 and the flow hole of the static valve plate 308 are periodically misaligned, thereby generating high-frequency pressure pulses.

[0064] The pendulum ball seat 403 is provided with radial holes, and a pendulum ball 404 is arranged in the pendulum ball seat 403. The pendulum ball 404 can move radially in the pendulum ball seat 403. The fluid drives the pendulum ball 404 to move centrifugally, and the pendulum ball 404 inertia impacts the inner wall of the pendulum ball seat 403 to form periodic radial vibration.

[0065] Embodiment 2

[0066] like Figure 2 As shown, in this example, the outlets of the second and third pairs of flow passages are blocked with seals 112. When the pressurized fluid flows from the upper end into the upper joint 101 of the flow conversion nipple, the fluid passes through the center hole, the spiral flow stabilizing block 103, the flow guide block 105, and then enters the piston assembly through the six parallel flow passages of the centering device 107 to reach the hole piston 108. Since four of the six passages through the hole piston 108 are blocked, the hole piston 108 will be subjected to an axial downward force, so the hole piston 108 and the hole piston 108 are in contact with each other. The guide pins 118 on the circumference of the orifice piston move downward (as shown in FIG. 8 ) until they contact the beveled edge between the peaks and troughs of the lower ratchet 111. Since the guide pins 118 can only move within the meshing area, the applied fluid pressure forces them to slide along the beveled edge, causing the orifice piston 108 to rotate until they enter the next trough of the lower ratchet 111. The guide pins 118 enter the next trough of the lower ratchet 111 from the trough of the upper ratchet 110, causing the orifice piston 108 to displace axially and rotate to the next position.

[0067] The axial displacement of the orifice piston 108 will also cause the spring 113 to be compressed and cause the lower end of the orifice piston 108 to contact the upper end of the flow channel conversion spindle 114. Since each of the three pairs of flow paths is colinearly aligned with the six opposite leakage channels, the entrances of the two pairs of opposite leakage channels are sealed. Since the pressurized fluid only enters the flow channel conversion spindle 114 through the first pair of channels of the orifice piston 108 and the other channels are blocked, there is only one pair of opposite leakage channels on the flow channel conversion spindle 114 to receive fluid inflow. Since only the first pair of flow channels are aligned with the first pair of leakage channels, only the first pair of opposing leakage channels receive fluid inflow. Since the entrances of the second and third pairs of leakage channels are blocked by seals, no fluid can flow into them.

[0068] After the pressurized fluid flows through the first pair of opposite flow passages, it enters the corresponding leakage passage of the passage conversion mandrel 114. After the first pair of leakage passages includes the first sub-passage and the second sub-passage, part of the pressurized fluid flows through the first sub-passage and flows out from the corresponding leakage hole. After part of the pressurized fluid flows through the corresponding second sub-passage, it will generate pressure on the baffle of the outlet valve plate 117. If the fluid pressure exceeds the critical value of overcoming the resistance of the outlet spring 116, the baffle will be pushed open, and the fluid enters the lower part of the tool through the outlet valve plate 117. Only a small amplitude vibration is generated when flowing through the first sub-passage and the second sub-passage. This is the "low amplitude" mode of the tool. At this time, the cross-section of the flow conversion short section 100 is as follows: Figure 2 shown.

[0069] When resetting, the interruption of the high pressure fluid flow releases the upward pressure of the spring 113, allowing it to loosen and move the orifice piston 108 upward. The initial position of the guide pin 118 is as shown in FIG. Figure 8c As shown, under the action of the upward force applied by the spring 113, the guide pins 118 move upward and hit the beveled edge between the peaks and troughs of the upper ratchet 110, and then they slide over the beveled edge, causing the hole-shaped piston 108 to rotate until it enters the next trough of the upper ratchet 110. This movement of the guide pins 118 from one trough of the lower ratchet 111 to the next trough of the upper ratchet 110 causes the hole-shaped piston 108 to be axially displaced and rotated upward.

[0070] Subsequently, the fluid flow is restored to place the guide pin 118 in the next trough of the lower ratchet 111 again, causing the orifice piston 108 to move axially downward, and further rotating the orifice piston 108 to the next position. The downward axial displacement of the orifice piston 108 causes the compression of the spring 113 again, and causes the lower end of the orifice piston 108 to contact the upper end of the channel conversion spindle 114, so that the first pair of flow channels of the orifice piston 108 are aligned with the second pair of leakage channels of the channel conversion spindle 114, and causes the entrances of the remaining two pairs of leakage channels to be blocked, and only the second pair of opposite leakage channels allows fluid to flow in.

[0071] After the pressurized fluid flows through the second pair of opposite leakage channels, it is ejected from the corresponding leakage ports on the lower cylindrical area of ​​the flow channel conversion mandrel 114 and flows into the lower part of the tool. Compared with the shock wave generated by the fluid flowing through the first pair of leakage channels, the shock wave generated by the fluid flowing through the second pair of leakage channels has a larger amplitude. This is the "high amplitude" mode of the tool. At this time, the cross-section of the flow conversion short section 100 is as follows: Fig. 9 shown.

[0072] In order to stop all vibrations generated when the pressurized fluid flows through the tool, the process of pressurized fluid flowing through the tool is interrupted and then resumed, similar to the above description, the interruption of fluid flow causes the spring 113 to be decompressed, the guide pin 118 to move from the trough of the lower ratchet 111 to the next trough of the upper ratchet, and the axial displacement and further rotation of the orifice piston 108, and the resumption of fluid flow again places the guide pin 118 in the next trough of the lower ratchet 111 and further rotates the orifice piston 108 to the next position, causing it to move downward again. The tool is shifted to align the first pair of flow passages of the orifice piston 108 with the third pair of leakage passages of the flow passage conversion mandrel 114, and the inlets of the other two pairs of leakage passages are blocked. Only the third pair of opposite leakage passages allows fluid to flow in. After the pressurized fluid flows through the third pair of leakage passages, it flows out from the corresponding leakage ports on the flow passage conversion mandrel 114. This is the "off" mode of the tool. The fluid flows through the third pair of leakage passages and then sprays out from the tool. The pressure of the fluid is very low and the shock wave generated can be ignored. At this time, the cross-section of the flow conversion nipple 100 is as follows: Fig.10 shown.

[0073] In the "low amplitude" mode or the "high amplitude" mode, the high-pressure fluid flows out of the flow conversion sub 100 and enters the lower part of the tool, and the high-pressure fluid flows into the axial vibration sub 200, the power sub 300, and the radial vibration sub 400 in sequence. When the fluid enters the power sub 300, the high-pressure fluid drives the screw rotor 304 to rotate at a high speed. Under the action of the rotor joint 305, the moving valve plate 307 is driven to make a circular motion around the static valve plate 308. When the overlapping area of ​​the moving valve plate 307 and the static valve plate 308 is the smallest, a large pressure pulse is generated. When the overlap area is the largest, a smaller pressure pulse is generated. The pressure pulse acts on the piston of the axial oscillation short section 200, causing the piston to reciprocate up and down in the wear-resistant bushing 205, generating axial vibration. When the flow area of ​​the dynamic and static valve holes becomes smaller, the pressure pulse increases, pushing the piston upward. When the flow area becomes larger, the pressure pulse decreases, and the piston moves downward under the action of the disc spring 204. The axial vibration of the piston is transmitted to the drill string, so that the friction between the drill string and the well wall is converted from static friction to dynamic friction, thereby reducing drilling friction and improving drilling pressure transmission efficiency.

[0074] At the same time, the pressure pulse generated by the rotation of the screw rotor 304 will be transmitted to the lateral vibration short section 400. The change in fluid pressure causes the pendulum ball 404 to produce centrifugal motion. The pendulum ball 404 inertia impacts the inner wall of the pendulum ball seat 403, generating a lateral periodic oscillation force, which converts the static friction resistance of sliding drilling into dynamic friction resistance, thereby achieving the purpose of reducing friction resistance and relieving support pressure.

[0075] The above embodiments are only used to illustrate the technical solutions of the present invention rather than to limit the same. Although the present invention has been described in detail with reference to the embodiments, a person skilled in the art should understand that the specific implementation modes of the present invention can still be modified or replaced by equivalents, and any modification or equivalent replacement that does not depart from the spirit and scope of the present invention should be included in the scope of the claims of the present invention.

Claims

1. A variable amplitude hydraulic oscillator, characterized in that: include: A flow conversion short section (100), an axial vibration short section (200), a power short section (300), and a radial vibration short section (400), wherein the flow conversion short section (100), the axial vibration short section (200), the power short section (300), and the radial vibration short section (400) are sequentially connected by pipe thread sealing; The flow conversion nipple (100) comprises an upper joint (101) of the flow conversion nipple, a lower joint (102) of the flow conversion nipple, a flow stabilizing assembly, a piston assembly, and a flow conversion assembly, wherein the flow stabilizing assembly is threadedly connected to the upper joint (101) of the flow conversion nipple, the piston assembly is fixed to the upper end of the lower joint (102) of the flow conversion nipple, and the flow conversion assembly is threadedly connected to the lower joint (102) of the flow conversion nipple; The flow stabilizing assembly comprises a spiral flow stabilizing block (103), a flow guide block (105), a tubular cup (104), and a centering device (107); the spiral flow stabilizing block (103) is installed inside the upper joint (101) of the flow conversion short joint; the flow guide block (105) is concentrically connected to the tubular cup (104) through a thread; the tubular cup (104) is threadedly connected to the centering device (107); and the centering device (107) is threadedly connected to the upper joint (101) of the flow conversion short joint; The piston assembly comprises a piston stabilizing rod (106), a hole-shaped piston (108), an upper ratchet (110), a lower ratchet (111), a ratchet sleeve (109), a sealing element (112), and a spring (113); the piston stabilizing rod (106) is threadedly connected to the hole-shaped piston (108) and passes through the center hole of the centering device (107); the hole-shaped piston (108) is installed in the upper ratchet (110) and the lower ratchet (111); the upper ratchet (110) and the lower ratchet (111) are installed in the ratchet sleeve (109) in a matching manner; the ratchet sleeve (109) is axially fixed through the lower end surface of the upper joint (101) of the flow conversion short section and the upper end surface of the flow channel conversion spindle (114); and the spring (113) is installed between the hole-shaped piston (108) and the flow channel conversion spindle (114); The flow conversion assembly comprises a flow channel conversion spindle (114), an outlet base (115), an outlet spring (116), and an outlet valve plate (117); the flow channel conversion spindle (114) is installed inside the flow conversion nipple lower joint (102) and is axially positioned by an internal protrusion; the outlet base (115) is threadedly connected to the lower end of the flow channel conversion spindle (114); and the outlet spring (116) is installed between the outlet base (115) and the outlet valve plate (117); The axial vibration pup joint (200) comprises a transmission spindle (201), a sliding sleeve (202), an axial vibration pup joint upper joint (203), a disc spring (204), a wear-resistant bushing (205), a piston shaft (206), a first piston (207), a second piston (208), and an axial vibration pup joint lower joint (209); the transmission spindle (201) is threadedly connected to the flow conversion pup joint lower joint (102); the sliding sleeve (202), the axial vibration pup joint upper joint (203), the wear-resistant bushing (205), and the axial vibration pup joint lower joint (209) are sequentially threadedly connected; the disc spring (204) is mounted on the transmission spindle (201); the piston shaft (206) is threadedly connected to the transmission spindle (201); and the first piston (207) and the second piston (208) are mounted outside the piston shaft (206); The power sub (300) comprises a first joint (301), an upper joint (302) of the power sub, a screw sleeve (303), a screw rotor (304), a rotor joint (305), a movable valve plate (307), and a static valve plate (308); the upper joint (302) of the power sub is threadedly connected to the first joint (301); the screw sleeve (303) is threadedly connected to the upper joint (302) of the power sub; the screw rotor (304) is located in a spiral cavity of the screw sleeve (303); the lower end of the screw rotor (304) is connected to the movable valve plate (307) through the rotor joint (305); and the static valve plate (308) is fixedly connected to the screw sleeve (303); The radial vibration pup joint (400) comprises a second joint (401), a radial vibration pup joint housing (402), a swing ball seat (403), and a swing ball (404); the second joint (401) is threadedly connected to the screw sleeve (303); the radial vibration pup joint housing (402) is threadedly connected to the second joint (401); the swing ball seat (403) is installed inside the radial vibration pup joint housing (402); and the swing ball (404) is installed inside the swing ball seat (403).

2. A variable amplitude hydraulic oscillator as claimed in claim 1, characterized in that: The guide block (105) has a wedge-shaped flow channel.

3. A variable amplitude hydraulic oscillator as claimed in claim 1, characterized in that: The hole-shaped piston (108) has three pairs of opposite flow passages, and the flow passage conversion spindle (114) has three pairs of opposite leakage channels, each pair of opposite leakage channels has an inlet and an outlet, and the outlet of each pair of opposite flow passages of the hole-shaped piston (108) is aligned with the inlet of each pair of opposite leakage channels of the flow passage conversion spindle (114) and extends to the outlet of the leakage channel.

4. A variable amplitude hydraulic oscillator as claimed in claim 1, characterized in that: A pair of mutually matching upper ratchet wheels (110) and lower ratchet wheels (111) are installed in the ratchet sleeve (109); the upper ratchet wheels (110) and the lower ratchet wheels (111) are rotationally fixed to the ratchet sleeve (109) via a sliding key; the hole-shaped piston (108) is axially movable relative to the upper ratchet wheels (110), the lower ratchet wheels (111) and the ratchet sleeve (109); the upper ratchet wheels (110) and the lower ratchet wheels (111) both have relative irregular edge surfaces with wave crests and wave troughs; the hole-shaped piston (108) has protrusions on its circumference, and the protrusions extend to the outer surfaces of the upper ratchet wheels (110) and the lower ratchet wheels (111).

5. A variable amplitude hydraulic oscillator as claimed in claim 3, characterized in that: The outlets of the three pairs of flow passages of the hole-shaped piston (108) are all provided with internal threads, and the outlets of the second pair of flow passages and the third pair of flow passages are respectively screwed into a pair of the sealing members (112) for sealing, and the four sealing members (112) are all composed of screws, and the screws are provided with an annular sealing rubber ring covering part of the thread of the screw head.

6. A variable amplitude hydraulic oscillator as claimed in claim 3, characterized in that: The flow channel conversion mandrel (114) comprises three pairs of drainage channels inside, the first pair of drainage channels comprises two outlets, the outlets of the second pair of drainage channels are located inside the tool, and the outlets of the third pair of drainage channels are aligned with the drainage outlets of the tool.

7. A variable amplitude hydraulic oscillator as claimed in claim 1, characterized in that: The end of the flow channel conversion spindle (114) is provided with an outlet valve plate (117) connected to the outlet spring (116).

8. A variable amplitude hydraulic oscillator as claimed in claim 1, characterized in that: The first piston (207) and the second piston (208) are contained in the axial vibration short section (200).

9. A variable amplitude hydraulic oscillator as claimed in claim 1, characterized in that: The upper end surface of the movable valve plate (307) is provided with a liquid inlet chamber, and the peripheral wall of the liquid inlet chamber is provided with a plurality of liquid inlet holes (306) arranged at equal angles. The movable valve plate (307) is provided with an eccentric hole, and the static valve plate (308) is provided with a flow hole.

10. A variable amplitude hydraulic oscillator as claimed in claim 1, characterized in that: The swing ball seat (403) is provided with a radial hole, and a swing ball (404) is arranged inside the swing ball seat (403).

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