CN109372424B

CN109372424B - Composite impact speed-increasing drilling tool for coiled tubing

Info

Publication number: CN109372424B
Application number: CN201811522211.6A
Authority: CN
Inventors: 许福东; 谭超; 董立; 张磊
Original assignee: Yangtze University
Current assignee: Yangtze University
Priority date: 2018-12-13
Filing date: 2018-12-13
Publication date: 2023-09-29
Anticipated expiration: 2038-12-13
Also published as: CN109372424A

Abstract

The invention relates to a composite impact speed-increasing drilling tool for a continuous oil pipe, belonging to the technical field of petroleum underground equipment. The composite impact accelerating drilling tool consists of a vibration pup joint, an oscillation pup joint and an impact pup joint; one end threaded connection of vibration nipple joint has vibration nipple joint: the other end of the oscillating nipple is provided with a drill bit assembly through a percussion nipple in threaded connection; the impact short circuit consists of a shell, a hydraulic hammer, a rotating shaft and a throttle valve seat; a rotating shaft is movably arranged in the shell through a limit screw and a ball; one end of the rotating shaft is provided with a compression sleeve in a threaded manner; a diversion sleeve is fixedly arranged in the shell at one side of the compaction sleeve through a diversion sleeve; the compression sleeve is provided with a bearing through a locking sleeve; one side of the locking sleeve is connected with a fixing sleeve in a threaded manner. The continuous oil pipe is provided with a composite impact speed-increasing drilling tool; the problems of low drilling speed and high drill bit abrasion caused by the fact that the existing underground drilling tool only drills in a single action mode are solved; meets the requirements of oilfield production and use.

Description

Composite impact speed-increasing drilling tool for coiled tubing

Technical Field

The invention relates to a composite impact speed-increasing drilling tool for a continuous oil pipe, belonging to the technical field of petroleum underground equipment.

Background

In recent years, with the continuous deep exploration technology of various large oil fields, the complexity of the well body structure of the oil well is gradually increased, and the problems of increasing the number of long horizontal wells, large inclination, multi-branch horizontal wells and the like are brought forward new practical requirements for drilling engineering; how to realize the quick drilling problem is the focus of research related to petroleum industry. The complex well structure not only puts higher requirements on the drilling technology and method, but also leads the friction resistance between the petroleum drill string and the well wall to be obviously increased by a larger well inclination angle, reduces the transmission efficiency of the weight on bit and influences the mechanical drilling speed. The existing underground drilling tool has the problems of low drilling speed and high drill bit abrasion caused by the fact that the existing underground drilling tool can only drill in a single action mode due to the limitation of structural reasons; the production requirements of enterprises cannot be met; therefore, it is necessary to develop a composite impact speed-increasing drilling tool for continuous oil pipe, which can drill by oscillating and reciprocating motion, so as to solve the above problems existing in the existing drilling tools.

Disclosure of Invention

The invention aims at: aiming at the defects of the prior art, the composite impact acceleration drilling tool for the coiled tubing, which can solve the problems of low drilling speed and high drill bit abrasion existing in the existing downhole drilling tool, is provided.

The technical scheme of the invention is as follows:

a composite impact accelerating drilling tool for a continuous oil pipe is composed of a vibration nipple, an oscillation nipple and an impact nipple; one end of the oscillation nipple is connected with the oscillation nipple in a threaded manner; the method is characterized in that: the other end of the oscillating nipple is provided with a drill bit assembly through a percussion nipple in threaded connection; the impact short circuit consists of a shell, a flow guiding sleeve, a flow dividing sleeve, a central throttling sleeve, a reversing valve core, a hydraulic hammer, a rotating shaft and a throttling valve seat; a rotating shaft is movably arranged in the shell through a limit screw and a ball; one end of the rotating shaft is provided with a compression sleeve in a threaded manner; a diversion sleeve is fixedly arranged in the shell at one side of the compaction sleeve through a diversion sleeve; the shunt sleeve is movably connected with the compression sleeve in an inserting way; the compression sleeve is provided with a bearing through a locking sleeve; one side of the locking sleeve is connected with a fixed sleeve in a threaded manner; the fixed sleeve is connected with the shunt sleeve through a guide screw; a buffer disc spring is arranged between the fixed sleeve and the shunt sleeve; a central throttling sleeve is pressed between the pressing sleeve and the rotating shaft through a throttling valve seat; the annular space between the central throttling sleeve and the rotating shaft is movably provided with a reversing valve core and a hydraulic hammer in sequence.

The circumference surface of the central throttling sleeve is movably provided with a reversing valve core through a guide flange; a certain gap is reserved between the reversing valve core and the central throttling sleeve; one end of the central throttling sleeve is provided with a pressure-holding conical surface; one end of the central throttling sleeve is fixedly connected with the rotating shaft through a throttling valve seat.

The outer surface of the flow guiding sleeve is of a ladder-shaped structure; the outer surface of the guide sleeve is provided with external threads; the guide sleeve is arranged in one end of the shell through external threads; the inside of one end of the guide sleeve is conical; the diversion sleeve is provided with a diversion sleeve in a threaded manner; a certain gap is reserved between the outer surface of the thin end of the flow guiding sleeve and the flow dividing sleeve.

The outer surface of the split sleeve is of a ladder-shaped structure; the shunt sleeve is sleeved with a fixed sleeve; a certain gap is reserved between the outer surface of the split sleeve and the outer surface of the fixed sleeve and the inner wall of the shell; the fixed sleeve is connected with a guide screw through threads; the guide screw is in sliding connection with a guide groove arranged on the shunt sleeve; one end of the shunt sleeve is provided with a diversion hole A; the shell is communicated with the inside of the split sleeve through a diversion hole A.

The outer surface and the inner part of the compression sleeve are both stepped; a certain gap is reserved between the inner stepped part of the compression sleeve and the end head of the shunt sleeve; the compaction sleeve is provided with a diversion hole B; a certain gap is reserved between the inner wall of the compression sleeve and the central throttling sleeve; the shell is communicated with the reversing valve core and the hydraulic hammer through a gap between the diversion hole B and the compression sleeve as well as the central throttling sleeve.

The rotating shaft is of a hollow shaft structure; one end of the rotating shaft is provided with a mounting flange; limiting blocks are uniformly distributed on the inner side of the mounting flange; the rotating shaft is movably clamped and connected with the end head of the shell through a limiting block; the circumference of the rotating shaft is provided with a limit ring groove, and the rotating shaft is movably connected with the shell through a limit screw and a ball; the inside of the rotating shaft is symmetrically provided with inwards concave connecting parts; inner low-pressure grooves are symmetrically formed on the inner wall of the rotating shaft between the connecting parts; a plurality of high-pressure transmission holes are respectively arranged on the rotating shafts at the two sides of the inner low-pressure groove; four outer high-pressure grooves are uniformly distributed on the circumferential surface of the rotating shaft; one end of the outer high-pressure groove extends to the end part of the rotating shaft; the outer high-pressure grooves are respectively communicated with the corresponding high-pressure transmission holes; the outer high-pressure groove is communicated with the shell through a guide groove arranged on the pressing sleeve.

The hydraulic hammer is cylindrical, and outer limit strips with circular arc surfaces are symmetrically arranged on the circumferential surface of the hydraulic hammer; the hydraulic hammers on two sides of the outer limit strip are respectively provided with a pressure guide hole A; an inner limit strip is arranged on the inner wall of the hydraulic hammer in a cross shape with the outer limit strip; the hydraulic hammers on two sides of the inner limit strip are respectively provided with a pressure guide hole B; the circumference surface of the hydraulic hammer is in sliding connection with the inner wall of the rotating shaft; the outer limit bar of the hydraulic hammer is slidingly connected with the joint of the rotating shaft 66.

The reversing valve core is cylindrical; the circumference surface of the reversing valve core is symmetrically provided with inward concave assembly parts; the assembly part is in sliding connection with an inner limit bar of the hydraulic hammer; four groups of low-pressure grooves are uniformly distributed on the reversing valve core between the assembly parts; a diversion end hole is formed in the reversing valve core at one end of the low-pressure groove; a plurality of groups of pressure guide holes C are uniformly distributed on the reversing valve core between the low-pressure grooves.

The hydraulic hammer is in abutting connection with the rotating shaft in the clockwise direction; when the reversing valve core is in abutting connection with the hydraulic hammer in the clockwise direction; the high-pressure transmission holes positioned in the first quadrant and the third quadrant on the rotating shaft are communicated with the pressure guide hole B of the hydraulic hammer; the second and fourth quadrant high pressure transmission holes are in a sealing state with the hydraulic hammer; the two groups of inner low-pressure grooves on the rotating shaft are respectively communicated with the pressure guide holes B of the hydraulic hammer; at the moment, two groups of pressure guide holes C of the reversing valve core are respectively communicated with the pressure guide holes A of the hydraulic hammer; the two groups of pressure guide holes C are in sealing connection with the hydraulic hammer; the two groups of low-pressure grooves of the reversing valve core are respectively and hermetically connected with the inner wall of the hydraulic hammer; the two groups of low-pressure grooves are respectively communicated with the pressure guide hole A of the hydraulic hammer.

The hydraulic hammer is in abutting connection with the rotating shaft in the anticlockwise direction; when the reversing valve core is in abutting connection with the hydraulic hammer in the clockwise direction; the high-pressure transmission holes positioned in the first quadrant and the third quadrant on the rotating shaft are in sealing connection with the hydraulic hammer; the second and fourth quadrant high pressure transmission holes are communicated with the pressure guide holes B of the hydraulic hammer; the two groups of inner low-pressure grooves on the rotating shaft are respectively communicated with the pressure guide holes B of the hydraulic hammer; the pressure guide hole B is communicated with the assembling part of the reversing valve core; the two groups of pressure guide holes C of the reversing valve core are respectively communicated with the pressure guide holes A of the hydraulic hammer; the two groups of pressure guide holes C are in sealing connection with the hydraulic hammer; the two groups of low-pressure grooves of the reversing valve core are respectively and hermetically connected with the inner wall of the hydraulic hammer; the two groups of low-pressure grooves are respectively communicated with the pressure guide hole A of the hydraulic hammer.

The hydraulic hammer is in abutting connection with the rotating shaft in the anticlockwise direction; when the reversing valve core is in abutting connection with the hydraulic hammer in the anticlockwise direction; the high-pressure transmission holes positioned in the first quadrant and the third quadrant on the rotating shaft are in sealing connection with the hydraulic hammer; the second and fourth quadrant high pressure transmission holes are communicated with the pressure guide holes B of the hydraulic hammer; the two groups of inner low-pressure grooves on the rotating shaft are respectively communicated with the pressure guide holes B of the hydraulic hammer; the two groups of pressure guide holes C of the reversing valve core are respectively communicated with the pressure guide holes A of the hydraulic hammer; the two groups of pressure guide holes C are in sealing connection with the hydraulic hammer; the two groups of low-pressure grooves of the reversing valve core are respectively and hermetically connected with the inner wall of the hydraulic hammer; the two groups of low-pressure grooves are respectively communicated with the pressure guide hole A of the hydraulic hammer.

The hydraulic hammer is in abutting connection with the rotating shaft in the clockwise direction; when the reversing valve core is in abutting connection with the hydraulic hammer in the anticlockwise direction; the high-pressure transmission holes positioned in the first quadrant and the third quadrant on the rotating shaft are communicated with the pressure guide hole B of the hydraulic hammer; the second and fourth quadrant high pressure transmission holes are in a sealing state with the hydraulic hammer; the two groups of inner low-pressure grooves on the rotating shaft are respectively communicated with the pressure guide holes B of the hydraulic hammer; the pressure guide hole B is communicated with the assembly part; the two groups of pressure guide holes C of the reversing valve core are respectively communicated with the pressure guide holes A of the hydraulic hammer; the two groups of pressure guide holes C are in sealing connection with the hydraulic hammer; the two groups of low-pressure grooves of the reversing valve core are respectively and hermetically connected with the inner wall of the hydraulic hammer; the two groups of low-pressure grooves are respectively communicated with the pressure guide hole A of the hydraulic hammer.

The invention has the beneficial effects that:

the composite impact speed-increasing drilling tool for the continuous oil pipe is ingenious in design and can realize hydraulic axial vibration and radial vibration; the problems of low drilling speed and high drill bit abrasion caused by the fact that the existing underground drilling tool only drills in a single action mode are solved; meets the requirements of oilfield production and use.

Drawings

FIG. 1 is a schematic diagram of a front view of the present invention;

FIG. 2 is a schematic diagram of the front view of an impact shorting of the present invention;

FIG. 3 is an enlarged schematic view of FIG. 2A;

FIG. 4 is an enlarged schematic view of the structure shown at B in FIG. 2;

FIG. 5 is a schematic diagram of the front view of the rotating shaft of the present invention;

FIG. 6 is a schematic diagram of an axially measured structure of a rotating shaft according to the present invention;

FIG. 7 is a schematic view of the structure in the direction C-C in FIG. 5;

FIG. 8 is a schematic diagram of the axially measured structure of the hydraulic hammer of the present invention;

FIG. 9 is a schematic cross-sectional view of a hydraulic hammer of the present invention;

FIG. 10 is a schematic view of the reversing valve of the present invention;

FIG. 11 is a schematic diagram of the front view of the reversing valve of the present invention;

FIG. 12 is a schematic view of the structure in the direction D-D in FIG. 11;

FIG. 13 is a schematic structural view of the working states of the reversing valve core, the hydraulic hammer and the rotary shaft of the present invention;

FIG. 14 is a schematic structural view of the working states of the reversing valve core, the hydraulic hammer and the rotary shaft of the present invention;

FIG. 15 is a schematic structural view of the working states of the reversing valve core, the hydraulic hammer and the rotary shaft of the present invention;

FIG. 16 is a schematic structural view of the working states of the reversing valve core, the hydraulic hammer and the rotary shaft of the present invention;

FIG. 17 is a schematic view of the vibratory nipple of the present invention;

figure 18 is a schematic structural view of an oscillation nipple of the present invention,

figure 19 is a schematic cross-sectional view of a fluidic element of the present invention,

Figure 20 is a schematic view of the cross-sectional E-E configuration of figure 19,

figure 21 is a schematic view of the F-F cross-sectional structure of figure 19,

figure 22 is a schematic view of the G-G cross-sectional structure of figure 19,

figure 23 is a schematic cross-sectional view of the cylinder liner of the present invention,

figure 24 is a schematic cross-sectional view of figure 23,

figure 25 is a schematic cross-sectional view of the cylinder head of the present invention,

fig. 26 is a schematic cross-sectional structure of the cylinder head.

In the figure: 1. vibration nipple, 2, vibration nipple, 3, mandrel, 4, upper joint, 5, lower joint, 6, outer tube, 7, middle joint, 8, piston, 9, spacer, 10, push plate, 11, disc spring, 12, mandrel middle joint, 13, mandrel lower joint, 14, balance hole, 15, outer tube, 16, spline housing, 17, vibration nipple joint, 18, cylinder liner, 19, piston rod, 20, vibration piston, 21, spline shaft, 22, rotating housing, 23, vibration disc, 24, cylinder head, 25, mount pad, 26, middle plate, 27, left side plate, 28, right side plate, 29, lower communication hole, 30, upper communication hole, 31, wedge, 32, upper middle plate, 33, lower middle plate, 34, fluid inlet, 35, fluid outlet, 36, upper fluid flow chamber, 37, upper feedback fluid flow chamber, 38, upper feedback fluid flow channel, 39, lower fluid flow chamber, 40, lower feedback fluid flow chamber, 41, lower feedback runner, 42, piston cavity, 43, upper liquid inlet, 44, cylinder liner lower runner, 45, left runner, 46, right runner, 47, swivel bearing, 48, cylinder head left runner, 49, cylinder head right runner, 50, spiral trajectory, 51, rotating steel ball, 52, synchronizing sleeve, 53, sliding steel ball, 54, liquid flow port, 55, spline shaft center hole, 56, communication hole, 57, liquid flow hole, 58, impact short circuit, 59, drill bit assembly, 60, shell, 61, diversion sleeve, 62, sleeve, 63, central throttling sleeve, 64, reversing valve core, 65, hydraulic hammer, 66, rotating shaft, 67, throttling valve seat, 68, 69, ball, 70, compression sleeve, 71, screw, 72, fixed sleeve, 73, buffer disc spring, 74, locking sleeve, 75, diversion hole A,76, limit ring groove, 77, connecting part, 78, inner low pressure groove, 79, the high-pressure transmission hole, 80, an outer high-pressure groove, 81, an outer limit strip, 82, an inner limit strip, 83, pressure guiding holes A,84, pressure guiding holes B,85, an assembly part, 86, a low-pressure groove, 87, a flow guiding end hole, 88, pressure guiding holes C,89, a mounting flange, 90, a limit block, 91, a pressure-holding conical surface, 92, flow guiding holes B,93 and a guide groove.

Detailed Description

The composite impact accelerating drilling tool for the continuous oil pipe consists of a vibration nipple 1, an oscillation nipple 2 and an impact nipple 58; one end of the vibration nipple 2 is connected with a vibration nipple 1 through threads; the other end of the oscillation nipple 2 is provided with a drill bit assembly 59 (see fig. 1 of the specification) by a threaded impact nipple 58.

The impact short circuit 58 is composed of a shell 60, a flow guiding sleeve 61, a flow dividing sleeve 62, a central throttling sleeve 63, a reversing valve core 64, a hydraulic hammer 65, a rotating shaft 66 and a throttling valve seat 67 (see fig. 2 of the specification).

A rotating shaft 66 is movably arranged in the shell 60 through a limit screw 68 and a ball 69; the rotating shaft 66 is in a hollow shaft structure; the circumference of the rotating shaft 66 is provided with a limit ring groove 76, and the rotating shaft 66 is movably connected with the shell 60 through a limit screw 68 and a ball 69 (see fig. 2 and 5 in the specification); a portion of the balls 69 are located inside the retainer ring groove 76 and a portion are located inside the housing 60; the purpose of the ball 69 and the retainer groove 76 is to: so that the rotational shaft 66 can only be rotated and not axially guided by the balls 69 and the retainer ring grooves 76.

A mounting flange 89 is arranged at one end of the rotating shaft 66; a limiting block 90 (see fig. 5 and 6 in the specification) is uniformly distributed on the inner side of the mounting flange 89; the rotating shaft 66 is movably clamped and connected with the end of the shell 60 through a limiting block 90 (not shown in the drawing in the specification); the purpose of the mounting flange 89 and stopper 90 being so arranged is: so that the rotating shaft 66 can only rotate reciprocally in the housing 60 under the limiting action of the limiting block 90; thus, the purpose that the rotating shaft 66 drives the drill bit assembly 59 to rotate reciprocally when in operation is achieved.

The rotating shaft 66 is internally symmetrically provided with an inwardly concave engagement portion 77; inner low-pressure grooves 78 (see fig. 6 and 7 of the specification) are symmetrically formed on the inner wall of the rotating shaft 66 between the engagement portions 77; the inner low pressure groove 78 extends to the end of the rotating shaft 66 and communicates with the low pressure space on one side of the throttle valve seat 67; whereby in operation the drilling fluid on the side of the throttle valve seat 67 will fill the inner low pressure groove 78.

The rotating shafts 66 on both sides of the inner low pressure groove 78 are respectively provided with a plurality of high pressure transmission holes 79; four outer high-pressure grooves 80 are uniformly distributed on the circumferential surface of the rotating shaft 66; one end of the outer high pressure groove 80 extends to an end portion of the rotating shaft 66; the outer high-pressure grooves 80 communicate with the corresponding high-pressure transmitting holes 79, respectively (see fig. 6 and 7 of the specification).

The outer high-pressure groove 80 communicates with the housing 60 through a guide groove provided on the pressing sleeve 70 (not shown in the drawing of the specification). In operation, drilling fluid within the housing 60 will flow through the guide channels on the compression sleeve 70 into the outer high pressure groove 80 and through the high pressure transfer port 79 into the interior of the rotating shaft 66.

A compression sleeve 70 (see fig. 2 of the specification) is screwed on one end of the rotating shaft 66; the compression sleeve 70 is fixedly connected relative to the rotational shaft 66; the rotation shaft 66 can drive the pressing sleeve 70 to synchronously rotate when in action.

The outer surface and the inner portion of the compression sleeve 70 are stepped (see fig. 4 of the specification);

the inner stepped portion of the compression sleeve 70 is spaced from the end of the split sleeve 62 by a gap; the pressing sleeve 70 is provided with a diversion hole B92 (see fig. 4 of the specification).

A certain gap exists between the inner wall of the compression sleeve 70 and the central throttling sleeve 63; housing 60 communicates with a reversing valve cartridge 64 and a hydraulic ram 65 through a pilot orifice B92 and a gap between a compression sleeve 70 and a center throttle sleeve 63 (see fig. 4 of the specification). The purpose of this arrangement is that: so that in operation the drilling fluid of the housing 60 can enter the interior of the reversing valve cartridge 64 and the hydraulic hammer 65 from the end face through the gap between the pilot bore B92, the compression sleeve 70 and the center throttling sleeve 63.

A diversion sleeve 62 is fixedly arranged in the shell 60 at one side of the pressing sleeve 70 through a diversion sleeve 61; the split sleeve 62 is movably inserted into the compression sleeve 70 (see fig. 2 and 3 of the description).

The outer surface of the guide sleeve 61 is in a ladder-shaped structure; the outer surface of the guide sleeve 61 is provided with external threads; the guide sleeve 61 is mounted in one end of the housing 60 by external threads, so that the guide sleeve 61 and the housing 60 are kept in relatively fixed connection.

The inner part of one end of the guide sleeve 61 is conical (see fig. 3 of the specification); the purpose of the deflector 61 is to: so that the drilling fluid passing through the inside of the diversion sleeve 61 during operation reduces the flow area through the conical part, thereby achieving the purpose of enhancing the drilling fluid pressure to form high-pressure drilling fluid.

The diversion sleeve 61 is provided with a diversion sleeve 62 in a threaded manner; the outer surface of the shunt sleeve 62 is in a ladder-shaped structure; one end of the shunt sleeve 62 is provided with a diversion hole A75; the housing 60 communicates with the interior of the splitter sleeve 62 through a deflector aperture a75 (see fig. 3 of the specification). A certain gap is reserved between the outer surface of the thin end of the guide sleeve 61 and the split sleeve 62 (see fig. 3 in the specification); the purpose of this arrangement is that: so that in operation the high pressure drilling fluid within the pod 61 may enter the housing 60 through the pod aperture a 75.

The split sleeve 62 is sleeved with a fixed sleeve 72; a certain gap exists between the outer surface of the split sleeve 62 and the outer surface of the fixed sleeve 72 and the inner wall of the shell 60 (see fig. 3 of the specification); the purpose of this arrangement is that: so that in operation high pressure drilling fluid can circulate through the gap.

The fixed sleeve 72 is connected with a guide screw 71 in a threaded manner; the guide screw 71 is slidingly connected with a guide groove 93 provided on the split sleeve 62 (see fig. 3 of the specification); the purpose of the guide screw 71 and the guide groove 93 being so arranged is that: firstly, the fixed sleeve 72 is limited by the guide screw 71 and the guide groove 93, so that the fixed sleeve moves axially relative to the split sleeve 62; preventing the deviation of the motion trail. Secondly, the problem that the guide screw 71 is sheared by the split sleeve 62 when the fixed sleeve 72 and the split sleeve 62 move relatively is prevented.

The compression sleeve 70 is provided with a bearing through a locking sleeve 74; the locking sleeve 74 is movably connected with the pressing sleeve 70 through a bearing (see fig. 4 of the specification); the locking sleeve 74 is in threaded connection with the fixed sleeve 72; a buffer disc spring 73 (see fig. 3 of the specification) is arranged between the fixed sleeve 72 and the split sleeve 62; the purpose of providing the buffer disc spring 73 is: so that the vibration of the diversion sleeve 61 and the diversion sleeve 62 can be transmitted to the fixed sleeve 72 through the buffer disc spring 73 during operation, thereby avoiding the problem of abrasion when the diversion sleeve 62 directly transmits the vibration to the fixed sleeve 72.

A central throttling sleeve 63 is pressed between the pressing sleeve 70 and the rotating shaft 66 through a throttling valve seat 67; the throttle valve seat 67 is provided with a flow hole (not shown in the drawings of the specification) inside.

One end of the central throttling sleeve 63 is provided with a pressure-holding conical surface 91 (see fig. 2 of the specification); the purpose of setting the pressure-holding conical surface 91 is that: the flow area of the central throttling sleeve 63 is reduced through the pressure-holding conical surface 91, so that the aim of enhancing the pressure inside the central throttling sleeve 63 is fulfilled; and in the process of leading the drilling fluid to pass through the central throttling sleeve 63 and enter the rotating shaft 66, the flow area in the rotating shaft 66 is increased, thereby achieving the purpose of reducing the drilling fluid pressure to form low-pressure drilling fluid in the rotating shaft 66.

One end of the center throttle sleeve 63 is fixedly connected with the rotating shaft 66 through a throttle valve seat 67. The circumference surface of the central throttling sleeve 63 is movably provided with a reversing valve core 64 through a guide flange; a certain gap exists between the reversing valve core 64 and the central throttling sleeve 63 (see fig. 3 of the specification); the purpose of this arrangement is that: so that in operation, high pressure drilling fluid pilot bore B92 in housing 60 enters the gap between center sleeve 63 and reversing valve core 64, which is filled with high pressure drilling fluid.

Reversing valve core 64 is cylindrical (see figures 10, 11 and 12 of the drawings); the circumferential surface of the reversing valve core 64 is symmetrically provided with an inwardly recessed fitting portion 85 (see fig. 12 of the specification).

Four groups of low-pressure grooves 86 are uniformly distributed on the reversing valve core 64 between the assembling parts 85; a diversion end hole 87 (see fig. 10 and 11 of the specification) is arranged on the reversing valve core 64 at one end of the low-pressure groove 86; in operation, the low pressure drilling fluid in the rotating shaft 66 at one end of the central throttling sleeve 63 can enter the low pressure groove 86 through the throttling valve seat 67 and the diversion end hole 87, so that the purpose of filling the low pressure groove 86 with the low pressure drilling fluid is achieved.

A plurality of groups of pressure guide holes C88 (see figure 12 of the specification) are uniformly distributed on the reversing valve core 64 between the low-pressure grooves 86; the pressure guiding hole C88 has the function of guiding flow.

A hydraulic hammer 65 (see fig. 2 of the specification) is movably sleeved on the reversing valve core 64; the hydraulic hammer 65 is cylindrical, and outer limit strips 81 with circular arc-shaped surfaces are symmetrically arranged on the circumferential surface of the hydraulic hammer 65 (see fig. 8 and 9 in the specification).

The hydraulic hammers 65 on both sides of the outer limit bar 81 are respectively provided with a pressure guide hole A83 (see fig. 8 and 9 of the specification); an inner limit bar 82 (see fig. 8 and 9 of the specification) is arranged on the inner wall of the hydraulic hammer 65 in a cross shape with the outer limit bar 81; the inner limit bar 82 of the hydraulic hammer 65 is in sliding connection with the assembly part 85 of the reversing valve core 64; when the hydraulic hammer 65 rotates relative to the reversing valve core 64, the reversing valve core 64 can limit the rotation amplitude of the hydraulic hammer 65 through the assembly part 85 and the inner limit strip 82.

The hydraulic hammers 65 on both sides of the inner limit bar 82 are respectively provided with a pressure guide hole B84 (see fig. 8 and 9 of the specification); the circumference of the hydraulic hammer 65 is in sliding connection with the inner wall of the rotating shaft 66; the outer limit 81 of the hydraulic hammer 65 is slidably connected to the engagement portion 77 of the rotary shaft 66 (see fig. 13 of the specification).

When the hydraulic hammer 65 is in a clockwise direction, the hydraulic hammer is in abutting connection with the rotating shaft 66; when the reversing valve core 64 is in abutting connection with the hydraulic hammer 65 in the clockwise direction, the continuous oil pipe is in the initial position by the composite impact speed-increasing drilling tool (see fig. 13 of the specification); at this time, the high-pressure transmission holes 79 on the rotating shaft 66 in the first quadrant and the third quadrant are communicated with the pressure guide hole B84 of the hydraulic hammer 65; the second, four-quadrant high-pressure-transmitting hole 79 is in a sealed state with the hydraulic hammer 65 (see fig. 13 of the specification); the two groups of inner low-pressure grooves 78 on the rotating shaft 66 are respectively communicated with pressure guide holes B84 of the hydraulic hammer 65 (see fig. 13 of the specification); at this time, two groups of pressure guide holes C88 of the reversing valve core 64 are respectively communicated with the pressure guide holes A83 of the hydraulic hammer 65; the two groups of pressure guide holes C88 are in sealing connection with the hydraulic hammer 65; two groups of low-pressure grooves 86 of the reversing valve core 64 are respectively connected with the inner wall of the hydraulic hammer 65 in a sealing way; the two sets of low-pressure grooves 86 are respectively communicated with the pressure guide holes a83 of the hydraulic hammer 65 (see fig. 13 of the specification).

In the above state, when drilling fluid enters the impact short 58, high-pressure drilling fluid between the center throttle sleeve 63 and the reversing valve core 64 enters the pressure guide hole a83 of the hydraulic hammer 65 through the pressure guide hole C88; the low pressure drilling fluid of the low pressure groove 86 in the reversing valve core 64 is communicated with the joint part 77 through the pressure guide hole A83; at this time, under the action of high pressure of the high-pressure drilling fluid, the hydraulic hammer 65 and the reversing valve core 64 are pushed to synchronously rotate anticlockwise; when the hydraulic hammer 65 rotates counterclockwise to collide with the engagement portion 77, the hydraulic hammer 65 stops rotating (see fig. 14 of the specification).

At this time, the hydraulic hammer 65 is in abutting connection with the rotating shaft 66 in the counterclockwise direction; when reversing valve cartridge 64 is in a counter-clockwise engagement with hydraulic hammer 65 (see fig. 14 of the specification); the high-pressure transmission holes 79 positioned in the first quadrant and the third quadrant on the rotating shaft 66 are in sealing connection with the hydraulic hammer 65; the second, four-quadrant high-pressure delivery hole 79 communicates with the pilot hole B84 of the hydraulic hammer 65 (see fig. 14 of the specification); the two groups of inner low-pressure grooves 78 on the rotating shaft 66 are respectively communicated with the pressure guide holes B84 of the hydraulic hammer 65; pilot orifice B84 communicates with fitting portion 85 of reversing valve cartridge 64 (see fig. 14 of the specification); the two groups of pressure guide holes C88 of the reversing valve core 64 are respectively communicated with the pressure guide holes A83 of the hydraulic hammer 65; the two groups of pressure guide holes C88 are in sealing connection with the hydraulic hammer 65; two groups of low-pressure grooves 86 of the reversing valve core 64 are respectively connected with the inner wall of the hydraulic hammer 65 in a sealing way; the two sets of low-pressure grooves 86 are respectively communicated with the pressure guide holes a83 of the hydraulic hammer 65 (see fig. 14 of the specification).

Then the high-pressure drilling fluid in the first and third quadrant high-pressure transmission holes 79 in the rotating shaft 66 enters between the inner limit strip 82 and the assembling part 85 of the hydraulic hammer 65 through the pressure guide holes B84 on the hydraulic hammer 65; at this time, the reversing valve core 64 is driven to rotate counterclockwise relative to the hydraulic hammer 65 by the high-pressure drilling fluid, and when the reversing valve core 64 rotates counterclockwise to collide with the hydraulic hammer 65, the reversing valve core 64 stops acting.

At this time, the hydraulic hammer 65 is in abutting connection with the rotating shaft 66 in the counterclockwise direction; reversing valve core 64 is in a counter-clockwise interference connection with hydraulic ram 65 (see fig. 15 of the specification); the high-pressure transmission holes 79 positioned in the first quadrant and the third quadrant on the rotating shaft 66 are in sealing connection with the hydraulic hammer 65; the second, four-quadrant high-pressure delivery hole 79 communicates with the pilot hole B84 of the hydraulic hammer 65 (see fig. 15 of the specification); the two groups of inner low-pressure grooves 78 on the rotating shaft 66 are respectively communicated with pressure guide holes B84 of the hydraulic hammer 65 (see fig. 15 of the specification); the two groups of pressure guide holes C88 of the reversing valve core 64 are respectively communicated with the pressure guide holes A83 of the hydraulic hammer 65; the two groups of pressure guide holes C88 are in sealing connection with the hydraulic hammer 65 (see figure 15 of the specification); two groups of low-pressure grooves 86 of the reversing valve core 64 are respectively connected with the inner wall of the hydraulic hammer 65 in a sealing way; the two sets of low-pressure grooves 86 communicate with the pressure guide holes a83 of the hydraulic hammer 65, respectively (see fig. 15 of the specification).

Subsequently, the high-pressure drilling fluid between the central throttle sleeve 63 and the reversing valve core 64 enters the pressure guide hole A83 of the hydraulic hammer 65 through the pressure guide hole C88; the low pressure drilling fluid of the low pressure groove 86 in the reversing valve core 64 is communicated with the joint part 77 through the pressure guide hole A83; at this time, under the action of high pressure of the high-pressure drilling fluid, the hydraulic hammer 65 and the reversing valve core 64 are pushed to synchronously rotate clockwise; when the hydraulic hammer 65 rotates counterclockwise to collide with the engagement portion 77, the hydraulic hammer 65 stops rotating (see fig. 16 of the specification).

At this time, the hydraulic hammer 65 is in abutting connection with the rotating shaft 66 in the clockwise direction; reversing valve cartridge 64 is in a counter-clockwise interference connection with hydraulic ram 65 (see fig. 16 of the specification); at this time, the high-pressure transmission holes 79 on the rotating shaft 66 in the first quadrant and the third quadrant are communicated with the pressure guide hole B84 of the hydraulic hammer 65; the second, four-quadrant high-pressure-transmitting hole 79 is in a sealed state with the hydraulic hammer 65 (see fig. 16 of the specification); the two groups of inner low-pressure grooves 78 on the rotating shaft 66 are respectively communicated with the pressure guide holes B84 of the hydraulic hammer 65; the pressure guide hole B84 communicates with the fitting portion 85 (see fig. 16 of the specification); the two groups of pressure guide holes C88 of the reversing valve core 64 are respectively communicated with the pressure guide holes A83 of the hydraulic hammer 65; the two groups of pressure guide holes C88 are in sealing connection with the hydraulic hammer 65; two groups of low-pressure grooves 86 of the reversing valve core 64 are respectively connected with the inner wall of the hydraulic hammer 65 in a sealing way; the two sets of low-pressure grooves 86 are respectively communicated with the pressure guide holes a83 of the hydraulic hammer 65 (see fig. 16 of the specification).

Then the high-pressure drilling fluid in the first and third quadrant high-pressure transmission holes 79 in the rotating shaft 66 enters between the inner limit strip 82 and the assembling part 85 of the hydraulic hammer 65 through the pressure guide holes B84 on the hydraulic hammer 65; at this time, the reversing valve core 64 is driven to rotate clockwise relative to the hydraulic hammer 65 under the action of the high-pressure drilling fluid, when the reversing valve core 64 rotates clockwise to be in contact with the hydraulic hammer 65, the reversing valve core 64 stops acting, and at this time, the hydraulic hammer 65 is in contact with the rotating shaft 66 in the clockwise direction; reversing valve core 64 is in abutting connection with hydraulic hammer 65 in the clockwise direction; so far the impact short 58 returns to its original state.

From the above description, it can be seen that hydraulic hammer 65 and reversing valve core 64 respectively make reciprocating alternating high-frequency motions clockwise and counterclockwise during the cyclic action; it generates periodic high frequency torque which is ultimately transmitted to the bit assembly 59 via the rotary shaft 66, thereby effecting energy output.

One end of the impact short circuit 58 is connected with an oscillation short section 2 through threads; the oscillating nipple 2 is composed of an outer pipe body 15, a spline housing 16, an oscillating nipple joint 17, a jet flow element, a cylinder sleeve 18, a piston rod 19, an oscillating piston 20, a spline shaft 21, a rotating sleeve 22, an oscillating disc 23 and a cylinder cover 24 (see fig. 18 in the specification).

One end of the outer pipe body 15 is in threaded connection with the lower joint 5 of the vibration nipple 1; the other end of the outer tube body 15 is provided with an oscillation nipple joint 17 through a spline housing 16 in a threaded manner; one end in the outer tube body 15 is fixedly provided with a mounting seat 25, and one side of the mounting seat 25 is fixedly provided with a jet element through a fixing bolt.

The jet flow element is rectangular and consists of a middle plate 26, a left side plate 27 and a right side plate 28 (see fig. 19, 20 and 21 of the specification), wherein the left side plate 27 is arranged on one side of the middle plate 26, a lower communication hole 29 (see fig. 21 of the specification) is arranged on the left side plate 27, and the right side plate 28 is arranged on the other side of the middle plate 26; the right side plate 28 is provided with an upper communication hole 30 (see fig. 21 of the specification); the middle plate 26, the left side plate 27 and the right side plate 28 are fixed to each other by screws.

The middle plate 26 is composed of a wedge 31, an upper middle plate 32 and a lower middle plate 33 (see fig. 19 of the specification), the upper middle plate 32 and the lower middle plate 33 are arranged in an up-down mode, a horn-shaped liquid flow inlet 34 is arranged at one end between the upper middle plate 32 and the lower middle plate 33, a V-shaped liquid flow outlet 35 is arranged at the other end, and the liquid flow inlet 34 is communicated with the liquid flow outlet 35; the liquid outlet 35 is internally provided with the wedge 31, and the wedge 31 is in a conical shape, and the liquid flowing in can be split into an upper part and a lower part under the action of the conical wedge because the wedge 31 is arranged in the liquid outlet 35.

An upper liquid flow cavity 36 (see fig. 19 of the specification) is arranged on the upper middle plate 32, the upper liquid flow cavity 36 is respectively communicated with an upper communication hole 30 and a liquid flow outlet 35 which are arranged on the right side plate 28 (see fig. 19 and 21 of the specification), an upper feedback liquid flow cavity 37 is arranged on the upper middle plate 28 on one side of the upper liquid flow cavity 36, an upper feedback flow channel 38 is arranged on the left side plate 27 corresponding to the upper feedback liquid flow cavity 37, one end of the upper feedback flow channel 38 is communicated with the upper feedback liquid flow cavity 37, and the other end of the upper feedback flow channel 38 is communicated with the liquid flow outlet 35; an upper feedback fluid chamber 37 communicates with the trailing end of the fluid inlet 34 (see figures 19 and 20 of the description).

The lower middle plate 33 is provided with a lower fluid flow chamber 39, the lower fluid flow chamber 39 is respectively communicated with a lower communication hole 29 and a fluid flow outlet 35 which are arranged on the left side plate 27 (see fig. 19 and 21 of the specification), the lower middle plate 33 on one side of the lower fluid flow chamber 39 is provided with a lower feedback fluid flow chamber 40, the right side plate 28 corresponding to the lower feedback fluid flow chamber 40 is provided with a lower feedback fluid flow channel 41, one end of the lower feedback fluid flow channel 41 is communicated with the lower feedback fluid flow chamber 40, and the other end of the lower feedback fluid flow channel 41 is communicated with the fluid flow outlet 35. The lower feedback fluid chamber 40 communicates with the trailing end of the fluid inlet 34 (see figures 19 and 21 of the description).

A piston rod 19 is arranged in the outer tube body 15 at one side of the jet element through a cylinder sleeve 18 and a cylinder cover 24 (see figure 18 of the specification), the cylinder sleeve 18 is a cylinder, a piston cavity 42 is arranged in the cylinder sleeve 18 (see figure 23 of the specification), an upper liquid inlet hole 43 is arranged on the cylinder sleeve 18 at the front end of the piston cavity 42, and the front end of the piston cavity 42 is communicated with a liquid flow outlet 35 through the upper liquid inlet hole 43 (see figure 18 of the specification); a cylinder liner lower flow passage 44 (see fig. 23 of the specification) is arranged on the cylinder liner 18 below the piston cavity 42, and one end of the cylinder liner lower flow passage 44 is communicated with the liquid flow outlet 35 (see fig. 18 of the specification); the other end of the liner lower flow passage 35 communicates with the rear end of the piston chamber 42 (see fig. 23 of the specification).

A left flow passage 45 is provided on one side of the circumference of the cylinder liner 18 (the left flow passage 45 is formed by a groove on the left side of the circumference of the cylinder liner 18 being fitted with the inner wall of the outer tube body 15) (see fig. 24 of the specification), the left flow passage 45 communicates with a lower communication hole 29 provided on the left side plate 27 (see fig. 21 of the specification), a right flow passage 46 is provided on the other side of the circumference of the cylinder liner 18 (the right flow passage 46 is formed by a groove on the right side of the circumference of the cylinder liner 18 being fitted with the inner wall of the outer tube body 15), and the right flow passage 46 communicates with an upper communication hole 30 provided on the right side plate 28 (see fig. 24 and 21 of the specification).

An oscillating piston 20 is arranged at one end head of a piston rod 19 in a piston cavity 42 through a fixed nut (see fig. 18 of the specification); the other end of the piston rod 19 extends to the outer end of the cylinder cover 24; a rotary bearing 47 is arranged between the cylinder cover 24 and the piston rod 19, and a sealing ring is arranged between the cylinder cover 24 on one side of the rotary bearing 47 and the piston rod 19 so as to ensure the sealing in the cylinder sleeve 18.

A left cylinder head flow passage 48 and a right cylinder head flow passage 49 (see fig. 25 and 26 of the specification) are provided on the circumference of the cylinder head 24 in correspondence with the left and right flow passages 45 and 46 of the cylinder liner 18, the left flow passage 45 being in communication with the left cylinder head flow passage 48, and the right flow passage 46 being in communication with the right cylinder head flow passage 49 (see fig. 24 and 26 of the specification).

A spline shaft 21 is arranged in the spline housing 16 and the oscillation nipple joint 17 at one side of the cylinder cover 24 through a rotating housing 22; a piston rod 19 extending to the outer end of the cylinder head 24 is screwed with the spline shaft 21. The spline shaft 21 is connected with the spline housing 16 by a sliding key; a spiral trajectory 50 is respectively arranged on the inner wall of the rotary sleeve 22 and the circumference of the spline shaft 21 corresponding to the inner wall, and a rotary steel ball 51 is arranged in the spiral trajectory 50; in order to maintain uniform arrangement of the rotating steel balls 51, the rotating steel balls 51 may be arranged by a cage to avoid the piling of the rotating steel balls 51 during operation. Ball bearings are arranged between the rotary sleeve 22 and the oscillation nipple joint 17 to ensure the flexibility of rotation of the rotary sleeve 22.

A sliding steel ball 53 is mounted on the spline shaft 21 at one side of the rotating sleeve 22 through a synchronizing sleeve 52 for supporting and sliding the spline shaft 21. The synchronizing sleeve 52 and the rotating sleeve 22 are respectively cylindrical bodies, mounting grooves are axially and uniformly distributed on the circumference of the synchronizing sleeve 52 and used for mounting the sliding steel balls 53, an oscillating disc 23 is fixedly arranged on one end port of the rotating sleeve 22, and a liquid flow port 54 is eccentrically arranged on the oscillating disc 23 (see figure 18 of the specification).

The spline shaft 21 is provided with a spline shaft center hole 55, and a communication hole 56 is radially provided on the circumference of the spline shaft 21 at one end of the spline shaft center hole 55, and the communication hole 56 communicates with the spline shaft center hole 55 (see fig. 18 of the specification). The communication hole 56 communicates with both the head left flow passage 48 and the head right flow passage 49.

A closure plate is arranged in the central hole of the oscillating nipple joint 17 at one side of the oscillating disc 23, a liquid flow hole 57 is eccentrically arranged on the closure plate, and the liquid flow hole 54 is in sliding sealing connection (intermittent contact connection) with the liquid flow hole 57 (see fig. 18 in the specification).

One end of the vibration nipple 2 is connected with a vibration nipple 1 (see the attached figure 1 of the specification) in a threaded manner; the vibration nipple 1 is composed of a mandrel 3, an upper joint 4, a lower joint 5, an outer pipe 6, an intermediate joint 7 and a piston 8 (see fig. 17 of the specification).

One end of the outer tube 6 is provided with a lower joint 5 through an intermediate joint 7 in a threaded manner, the other end of the outer tube 6 is provided with an upper joint 4 in a threaded manner, a mandrel 3 is arranged in the outer tube 6, one end of the mandrel 3 extends to the outer end of the upper joint 4, the mandrel 3 is a reducer tubular body, and the mandrel 3 is in sliding connection with the upper joint 4 (see figure 17 of the specification).

A disc spring 11 is arranged on the mandrel 3 in the outer tube 6 through a spacer bush 10 and a push plate 9; the push plate 11 is in sliding connection with the inner wall of the outer tube 6. The mandrel 3 in the middle joint 7 is provided with a piston 8 through a mandrel middle joint 12 and a mandrel lower joint 13, and the periphery of the piston 8 is in sliding connection with the inner wall of the middle joint 7; a sealing ring is arranged between the periphery of the piston 8 and the middle joint 7; to ensure tightness between the piston 8 and the intermediate joint 7.

The central spindle joint 12 and the lower central spindle joint 13 are respectively tubular bodies, and the central spindle joint 12 is in threaded connection with the central spindle 3; one end of the joint 12 in the mandrel is in threaded connection with the lower joint 13 of the mandrel, and the other end of the joint 12 in the mandrel is in contact connection with the push plate 10. Balance holes 14 are provided on the circumferences of the upper joint 4 and the intermediate joint 7, respectively, to ensure pressure balance inside and outside the outer tube 6 in operation. The vibration nipple 1 is in threaded connection with the vibration nipple 2 through a lower joint 5.

When the coiled tubing is matched with the coiled tubing, drilling fluid firstly enters the oscillating nipple 2 through a through hole in the middle of a mandrel 3 of the oscillating nipple 1, the drilling fluid entering the oscillating nipple 2 enters the jet element through a fluid inlet 34 of the jet element, and the drilling fluid enters and exits from the fluid inlet 34 in a horn shape, so that the drilling fluid has a certain flow limiting effect, forms high-pressure jet flow under the action of the fluid inlet 34 and then is ejected out through a fluid outlet 35. The drilling fluid at the upper part of the wedge 31 enters the piston cavity 42 at the front end of the oscillating piston 20 through the upper fluid inlet hole 43, the drilling fluid at the lower part of the wedge 31 is collected at the rear end face of the oscillating piston 20 through the cylinder sleeve lower flow passage 44 and forms pressure to act on the rear end face of the oscillating piston 20, meanwhile, as the volume of the cylinder sleeve lower flow passage 44 is small relative to the volume of the piston cavity 42, after the drilling fluid collected at the rear end face of the oscillating piston 20 is filled in the cavity, the pressure pushes the oscillating piston 20 to move forward (to the left end of the piston cavity 42); in this process, the front end surface of the oscillating piston 20 presses the drilling fluid in the piston chamber 42, forcing the drilling fluid in the piston chamber 42 to be discharged through the upper fluid intake hole 43.

While the drilling fluid is discharged from the upper fluid inlet hole 43 and the oscillating piston 20 moves forward, the oscillating piston 20 drives the spline shaft 21 to move forward through the piston rod 19, and as the spline shaft 21 is arranged on the oscillating nipple joint 17 through the rotary sleeve 22, a spiral trajectory 50 is respectively arranged on the inner wall of the rotary sleeve 22 and the circumference of the spline shaft 21 corresponding to the inner wall of the rotary sleeve 22, and a rotary steel ball 51 is arranged in the spiral trajectory 50; in the process of driving the spline shaft 21 to move forward by the piston rod 19, the rotary sleeve 22 starts to rotate under the action of the spiral trajectory 50 and the rotary steel ball 51 arranged in the spiral trajectory 50, so that the oscillating disc 23 is driven to rotate, and periodic closing and opening are generated between the liquid flow port 54 and the liquid flow hole 57.

During the forward movement of the oscillating piston 20, drilling fluid at the upper part of the wedge 31 does not enter the piston cavity 42 through the upper fluid inlet 43 any more; at this time, a part of the drilling fluid in the upper part of the wedge 31 and in the upper fluid inlet 43 enters the upper feedback fluid chamber 37 through the upper feedback flow channel 38, and another part of the drilling fluid enters the upper fluid chamber 36.

Because the upper feedback liquid flow cavity 37 is communicated with the tail end of the liquid flow inlet 34, after the drilling fluid entering the upper feedback liquid flow cavity 37 is converged with the drilling fluid continuously entering the liquid flow inlet 34, the drilling fluid is continuously converged at the rear end face of the oscillating piston 20 by the cylinder sleeve lower flow passage 44, so that the oscillating piston 20 continuously moves forward and moves to the extreme position.

Drilling fluid entering the upper liquid flow cavity 36 enters the center hole 55 of the spline shaft through the upper communication hole 30, the right runner 46, the cylinder cover right runner 49 and the communication hole 56; then is discharged through the liquid flow port 54 and the liquid flow hole 57, and the liquid flow port 54 and the liquid flow hole 57 are respectively arranged eccentrically; and the oscillating disk 23 rotates with the rotating sleeve 22; during the rotation of the oscillating disk 23, the liquid flow port 54 and the liquid flow hole 57 are periodically closed and opened; the flow area is thus periodically changed, so that a pressure pulse is formed, which can act against the vibration nipple 1 via the vibration nipple connection 17, the spline housing 16 and the outer tubular body 15.

In the process of periodically closing and opening the fluid flow port 54 and the fluid flow port 57, when the fluid flow port 54 and the fluid flow port 57 are closed (when the fluid flow port 54 and the fluid flow port 57 are in a dislocation state), the drilling fluid flow passage is integrally cut off; the drilling fluid in the vibration pup joint 1 is converged under the flow limiting effect of the fluid inlet 34 and acts on the right end face of the piston 8, and the piston 8 is pushed to move forwards (move rightwards) along with the pressure increase of the drilling fluid in the process; the piston 8 drives the joint 12 in the mandrel and the lower joint 13 of the mandrel to integrally move, so that the mandrel 3 is driven to extend out of the upper joint 4, and an axial impact force of the mandrel 3 is formed; the axial impact force is matched with the pressure pulse of the oscillation nipple 2 to drive the continuous oil pipe, so that static friction between the continuous oil pipe and a well wall can be converted into dynamic friction, and the friction direction is changed, thereby reducing energy loss caused by friction and playing a role in reducing friction resistance. The central spindle 3 extends out of the upper joint 4, and meanwhile, the joint 12 in the central spindle compresses the disc spring 11 through the push plate 9 to enable the disc spring 11 to elastically deform and store energy; when the disc spring 11 is compressed to a limit, the drilling fluid flow passage is integrally communicated when the fluid flow port 54 and the fluid flow hole 57 are opened (when the fluid flow port 54 and the fluid flow hole 57 are in a superposition state); drilling fluid enters the jet element again through the fluid inlet 34, at the moment, the drilling fluid pressure of the vibration nipple 1 is smaller than the tension of the disc spring 11, and the mandrel 3 is reset under the action of the disc spring 11.

The drilling fluid re-entering the jet element is split again into an upper part and a lower part under the action of the wedge 31. The drilling fluid at the lower part of the wedge 31 is in a full liquid state and does not enter the cylinder sleeve lower flow passage 44 any more, the drilling fluid at the upper part of the wedge 31 enters the piston cavity 42 through the upper liquid inlet hole 43 and acts on the front end face of the oscillating piston 20, and the oscillating piston 20 is pushed to return backward along with the increase of pressure, in the process of the oscillating piston 20, the rear end face of the oscillating piston 20 presses the drilling fluid in the piston cavity 42, so that the drilling fluid in the piston cavity 42 at the rear end of the oscillating piston 20 is forced to be discharged by the cylinder sleeve lower flow passage 44.

While the drilling fluid is discharged from the cylinder sleeve lower runner 44 and the oscillating piston 20 is reset in the backward direction, the oscillating piston 20 drives the spline shaft 21 to reset in the backward direction through the piston rod 19, and as the spline shaft 21 is arranged on the oscillating nipple joint 17 through the rotary sleeve 22, a spiral trajectory 50 is respectively arranged on the inner wall of the rotary sleeve 22 and the circumference of the spline shaft 21 corresponding to the inner wall of the rotary sleeve, and a rotary steel ball 51 is arranged in the spiral trajectory 50; in the process of driving the spline shaft 21 to move backwards by the piston rod 19, under the action of the spiral trajectory 50 and the rotating steel balls 51 arranged in the spiral trajectory 50, the rotating sleeve 22 starts to rotate reversely, so that the oscillating disc 23 is driven to rotate reversely, and periodic closing and opening are generated between the liquid flow port 54 and the liquid flow hole 57 again.

During the backward reset process of the oscillating piston 20, drilling fluid at the upper part of the wedge 31 continuously enters the piston cavity 42 through the upper fluid inlet 43; at this time, a part of the drilling fluid in the lower part of the wedge 31 and in the cylinder liner lower flow passage 44 enters the lower feedback flow chamber 40 through the lower feedback flow passage 41, and another part of the drilling fluid enters the lower flow chamber 39.

Because the lower fluid chamber 39 is communicated with the tail end of the fluid inlet 34, after the drilling fluid entering the lower fluid chamber 39 is converged with the drilling fluid continuously entering the fluid inlet 34, the drilling fluid enters through the upper fluid inlet 43 and is continuously converged in the piston chamber 42 at the front end of the oscillating piston 20, so that the oscillating piston 20 continuously moves backward and moves to the limit position.

Drilling fluid entering the lower fluid flow cavity 39 enters the spline shaft center hole 55 through the lower communication hole 29, the left flow passage 45, the cylinder cover left flow passage 48 and the communication hole 56; and then discharged through the fluid port 54 and the fluid hole 57, since the fluid flow port 54 and the fluid flow port 57 are eccentrically disposed, respectively; and the oscillating disk 23 rotates with the rotating sleeve 22; during the rotation of the oscillating disk 23, the liquid flow port 54 and the liquid flow hole 57 are periodically closed and opened; the flow area is thus periodically changed, so that a pressure pulse is formed, which can act against the vibration nipple 1 via the vibration nipple connection 17, the spline housing 16 and the outer tubular body 15, so that one working cycle is completed.

While the vibration nipple 1 and the vibration nipple 2 circularly work, pressure pulse and axial impact are generated, drilling fluid discharged through the liquid flow hole 57 of the vibration nipple 2 enters the impact nipple 58 through the vibration nipple joint 17, and finally is discharged through the drill bit assembly 59 after passing through the diversion sleeve 61, the diversion sleeve 62 and the central throttling sleeve 63.

In the above process, since the inside of one end of the diversion sleeve 61 is tapered, and one end of the central throttling sleeve 63 is provided with the pressure holding conical surface 91, the flow area of the drilling fluid is reduced, and the pressure of the drilling fluid inside the diversion sleeve 61 and the central throttling sleeve 63 is further enhanced, so that the drilling fluid forms high pressure drilling fluid. When the high-pressure drilling fluid flows out of the central throttling sleeve 63 and enters the rotating shaft 66, the flow area in the rotating shaft 66 is increased, so that the drilling fluid pressure is reduced to form low-pressure drilling fluid in the rotating shaft 66; the resulting low pressure drilling fluid eventually drains through the drill bit assembly 59.

The high-pressure drilling fluid in the central throttling sleeve 63 enters the shell 60 through a gap between the diversion sleeve 61 and the diversion sleeve 62 and the diversion hole A75; part of the high-pressure drilling fluid entering the shell 60 flows into the outer high-pressure groove 80 of the rotating shaft 66 through the guide groove on the pressing sleeve 70, so that each high-pressure transmission hole 79 is always filled with the high-pressure drilling fluid, and the other part of the high-pressure drilling fluid enters a gap between the central throttling sleeve 63 and the reversing valve core 64 through the guide hole B92, so that four groups of pressure guide holes C88 in the reversing valve core 64 are filled with the high-pressure drilling fluid.

Part of the low-pressure drilling fluid in the rotating shaft 66 enters the four groups of low-pressure grooves 78 of the rotating shaft 66, and the other part enters the four groups of low-pressure grooves 86 of the reversing valve core 64 through the throttle valve seat 67 and the diversion end hole 87 so as to be filled with the low-pressure drilling fluid; the remaining low pressure drilling fluid is discharged through the drill bit assembly 59.

When drilling fluid enters the impact short circuit 58, the hydraulic hammer 65 and the reversing valve core 64 are at the initial positions, namely the hydraulic hammer 65 is in abutting connection with the rotating shaft 66 in the clockwise direction; reversing valve core 64 is in the clockwise direction and is a hydraulic hammer 65 (see fig. 13 of the specification); the high-pressure transmission holes 79 on the rotating shaft 66 in the first quadrant and the third quadrant are communicated with the pressure guide hole B84 of the hydraulic hammer 65; the second, four-quadrant high-pressure-transmitting hole 79 is in a sealed state with the hydraulic hammer 65 (see fig. 13 of the specification); the two groups of inner low-pressure grooves 78 on the rotating shaft 66 are respectively communicated with pressure guide holes B84 of the hydraulic hammer 65 (see fig. 13 of the specification); the two groups of pressure guide holes C88 of the reversing valve core 64 are respectively communicated with the pressure guide holes A83 of the hydraulic hammer 65; the two groups of pressure guide holes C88 are in sealing connection with the hydraulic hammer 65; two groups of low-pressure grooves 86 of the reversing valve core 64 are respectively connected with the inner wall of the hydraulic hammer 65 in a sealing way; the two sets of low-pressure grooves 86 are respectively communicated with the pressure guide holes a83 of the hydraulic hammer 65 (see fig. 13 of the specification).

In the above state, the high-pressure drilling fluid between the center throttle sleeve 63 and the reversing valve core 64 enters the pressure guide hole a83 of the hydraulic hammer 65 through the pressure guide hole C88; the low pressure drilling fluid of the low pressure groove 86 in the reversing valve core 64 is communicated with the joint part 77 through the pressure guide hole A83; at this time, under the action of high pressure of the high-pressure drilling fluid, the hydraulic hammer 65 and the reversing valve core 64 are pushed to synchronously rotate anticlockwise; when the hydraulic hammer 65 rotates counterclockwise to collide with the engagement portion 77, the hydraulic hammer 65 stops rotating (see fig. 14 of the specification).

At this time, the hydraulic hammer 65 is in abutting connection with the rotating shaft 66 in the counterclockwise direction; reversing valve core 64 is in a clockwise interference connection with hydraulic hammer 65 (see fig. 14 of the specification); the high-pressure transmission holes 79 positioned in the first quadrant and the third quadrant on the rotating shaft 66 are in sealing connection with the hydraulic hammer 65; the second, four-quadrant high-pressure delivery hole 79 communicates with the pilot hole B84 of the hydraulic hammer 65 (see fig. 14 of the specification); two sets of internal low pressure grooves 78 on the rotating shaft 66 respectively communicated with the pressure guide holes B84 of the hydraulic hammer 65; pilot orifice B84 communicates with fitting portion 85 of reversing valve cartridge 64 (see fig. 14 of the specification); the two groups of pressure guide holes C88 of the reversing valve core 64 are respectively communicated with the pressure guide holes A83 of the hydraulic hammer 65; the two groups of pressure guide holes C88 are in sealing connection with the hydraulic hammer 65; two groups of low-pressure grooves 86 of the reversing valve core 64 are respectively connected with the inner wall of the hydraulic hammer 65 in a sealing way; the two sets of low-pressure grooves 86 are respectively communicated with the pressure guide holes a83 of the hydraulic hammer 65 (see fig. 14 of the specification).

In this case the hydraulic hammer 65 is in the counter-clockwise direction to be connected with the rotating shaft 66 in a collision way; reversing valve core 64 is in a counter-clockwise interference connection with hydraulic ram 65 (see fig. 15 of the specification); at this time, the hydraulic hammer 65 is connected with the high-pressure transmission holes 79 on the rotating shaft 66 in a sealing way; the second, four-quadrant high-pressure delivery hole 79 communicates with the pilot hole B84 of the hydraulic hammer 65 (see fig. 15 of the specification); the two groups of inner low-pressure grooves 78 on the rotating shaft 66 are respectively communicated with pressure guide holes B84 of the hydraulic hammer 65 (see fig. 15 of the specification); the two groups of pressure guide holes C88 of the reversing valve core 64 are respectively communicated with the pressure guide holes A83 of the hydraulic hammer 65; the two groups of pressure guide holes C88 are in sealing connection with the hydraulic hammer 65 (see figure 15 of the specification); two groups of low-pressure grooves 86 of the reversing valve core 64 are respectively connected with the inner wall of the hydraulic hammer 65 in a sealing way; the two sets of low-pressure grooves 86 communicate with the pressure guide holes a83 of the hydraulic hammer 65, respectively (see fig. 15 of the specification).

The high-pressure drilling fluid between the central throttling sleeve 63 and the reversing valve core 64 then enters the pressure guide hole A83 of the hydraulic hammer 65 through the pressure guide hole C88; the low pressure drilling fluid of the low pressure groove 86 in the reversing valve core 64 is communicated with the joint part 77 through the pressure guide hole A83; at this time, under the action of high pressure of the high-pressure drilling fluid, the hydraulic hammer 65 and the reversing valve core 64 are pushed to synchronously rotate clockwise; when the hydraulic hammer 65 rotates counterclockwise to collide with the engagement portion 77, the hydraulic hammer 65 stops rotating (see fig. 16 of the specification).

The high pressure drilling fluid in the first and third quadrant high pressure transfer ports 79 in the shaft 66 is then rotated, the hydraulic hammer 65 enters between the inner limit strip 82 and the assembly part 85 of the hydraulic hammer 65 through the pressure guide hole B84 on the hydraulic hammer 65; at this time, the reversing valve core 64 is driven to rotate clockwise relative to the hydraulic hammer 65 under the action of the high-pressure drilling fluid, when the reversing valve core 64 rotates clockwise to be in contact with the hydraulic hammer 65, the reversing valve core 64 stops acting, and at this time, the hydraulic hammer 65 is in contact with the rotating shaft 66 in the clockwise direction; reversing valve core 64 is in abutting connection with hydraulic hammer 65 in the clockwise direction; so far the impact short 58 returns to its original state.

In the cyclic action process of the hydraulic hammer 65 and the reversing valve core 64, the hydraulic hammer 65 and the reversing valve core 64 respectively do clockwise and anticlockwise reciprocating alternating high-frequency motion; the device can generate periodic high-frequency torque, and the high-frequency torque is finally transmitted to the drill bit assembly 59 through the rotating shaft 66, so that the energy output is realized; thereby providing the drill bit assembly 59 with the ability to torsionally impact the rock breaking; the oscillation nipple 2 of the speed-increasing drilling tool has a pressure pulse function; the vibration nipple 1 has the function of axial impact, so that static friction between the continuous oil pipe and a well wall is converted into dynamic friction, and the friction direction is changed, thereby reducing energy loss caused by friction and friction resistance; the drill bit assembly 59 has the capability of axially impacting and breaking rock, so that the problems of low drilling speed and high drill bit abrasion caused by the fact that the existing underground drilling tool only drills in a single action mode are solved; meets the requirements of oilfield production and use.

Claims

1. A composite impact accelerating drilling tool for a continuous oil pipe is composed of a vibration nipple (1), an oscillation nipple (2) and an impact nipple (58); one end of the vibration nipple (2) is connected with the vibration nipple (1) through threads; the method is characterized in that: the other end of the oscillating nipple (2) is provided with a drill bit assembly (59) through an impact nipple (58) connected with the oscillating nipple through threads; the impact short circuit (58) consists of a shell (60), a flow guiding sleeve (61), a flow dividing sleeve (62), a central throttling sleeve (63), a reversing valve core (64), a hydraulic hammer (65), a rotating shaft (66) and a throttling valve seat (67); a rotating shaft (66) is movably arranged in the shell (60) through a limit screw (68) and a ball (69); one end of the rotating shaft (66) is provided with a compression sleeve (70) in a threaded manner; a diversion sleeve (62) is fixedly arranged in the shell (60) at one side of the compaction sleeve (70) through a diversion sleeve (61); the shunt sleeve (62) is movably connected with the compression sleeve (70) in a plug-in manner; the compression sleeve (70) is provided with a bearing through a locking sleeve (74); one side of the locking sleeve (74) is connected with a fixed sleeve (72) in a threaded manner; the fixed sleeve (72) is connected with the shunt sleeve (62) through a guide screw (71); a buffer disc spring (73) is arranged between the fixed sleeve (72) and the shunt sleeve (62); a central throttling sleeve (63) is pressed between the pressing sleeve (70) and the rotating shaft (66) through a throttling valve seat (67); annular space between the central throttling sleeve (63) and the rotating shaft (66) a reversing valve core (64) and a hydraulic hammer (65) are movably arranged in sequence;

The circumference surface of the central throttling sleeve (63) is movably provided with a reversing valve core (64) through a guide flange; a certain gap is reserved between the reversing valve core (64) and the central throttling sleeve (63); one end of the central throttling sleeve (63) is provided with a pressure-holding conical surface (91); one end of the central throttling sleeve (63) is fixedly connected with the rotating shaft (66) through a throttling valve seat (67);

the outer surface of the guide sleeve (61) is of a ladder-shaped structure; the outer surface of the guide sleeve (61) is provided with external threads; the guide sleeve (61) is arranged in one end of the shell (60) through external threads; the inside of one end of the guide sleeve (61) is conical; a diversion sleeve (62) is arranged on the diversion sleeve (61) in a threaded manner; a certain gap is reserved between the outer surface of the thin end of the guide sleeve (61) and the split sleeve (62);

the outer surface of the split sleeve (62) is of a ladder-shaped structure; a fixed sleeve (72) is sleeved on the shunt sleeve (62); a certain gap is reserved between the outer surface of the shunt sleeve (62) and the outer surface of the fixed sleeve (72) and the inner wall of the shell (60); the fixed sleeve (72) is connected with a guide screw (71) in a threaded manner; the guide screw (71) is in sliding connection with a guide groove (93) arranged on the shunt sleeve (62); one end of the shunt sleeve (62) is provided with a diversion hole A (75); the shell (60) is communicated with the inside of the diversion sleeve (62) through a diversion hole A (75);

The outer surface and the inner part of the compression sleeve (70) are both stepped; a certain gap is reserved between the inner step part of the compression sleeve (70) and the end head of the flow dividing sleeve (62); the compaction sleeve (70) is provided with a diversion hole B (92); a certain gap is reserved between the inner wall of the compression sleeve (70) and the central throttling sleeve (63); the shell (60) is communicated with the reversing valve core (64) and the hydraulic hammer (65) through a gap between the diversion hole B (92) and the compression sleeve (70) and the central throttling sleeve (63);

the rotating shaft (66) is of a hollow shaft structure; a mounting flange (89) is arranged at one end head of the rotating shaft (66); limiting blocks (90) are uniformly distributed on the inner side of the mounting flange (89); the rotating shaft (66) is movably clamped and connected with the end of the shell (60) through a limiting block (90); the circumference of the rotating shaft (66) is provided with a limit ring groove (76), and the rotating shaft (66) is movably connected with the shell (60) through a limit screw (68) and a ball (69); the inside of the rotating shaft (66) is symmetrically provided with an inward concave connecting part (77); inner low-pressure grooves (78) are symmetrically arranged on the inner wall of the rotating shaft (66) between the connecting parts (77); a plurality of high-pressure transmission holes (79) are respectively arranged on the rotating shafts (66) at two sides of the inner low-pressure groove (78); four outer high-pressure grooves (80) are uniformly distributed on the circumferential surface of the rotating shaft (66); one end of the outer high-pressure groove (80) extends to the end part of the rotating shaft (66); the outer high-pressure grooves (80) are respectively communicated with the corresponding high-pressure transmission holes (79); the outer high-pressure groove (80) is communicated with the shell (60) through a guide groove arranged on the compression sleeve (70);

The hydraulic hammer (65) is cylindrical, and outer limit strips (81) with circular arc surfaces are symmetrically arranged on the circumferential surface of the hydraulic hammer (65); the hydraulic hammers (65) on two sides of the outer limit bar (81) are respectively provided with a pressure guide hole A (83); an inner limit bar (82) is arranged on the inner wall of the hydraulic hammer (65) in a cross shape with the outer limit bar (81); the hydraulic hammers (65) on two sides of the inner limit strip (82) are respectively provided with a pressure guide hole B (84); the circumference of the hydraulic hammer (65) is in sliding connection with the inner wall of the rotating shaft (66); an outer limit bar (81) of the hydraulic hammer (65) is in sliding connection with a joint part (77) of the rotating shaft (66);

the reversing valve core (64) is cylindrical; the circumference surface of the reversing valve core (64) is symmetrically provided with inward concave assembling parts (85); the assembly part (85) is in sliding connection with an inner limit strip (82) of the hydraulic hammer (65); four groups of low-pressure grooves (86) are uniformly distributed on the reversing valve core (64) between the assembly parts (85); a plurality of groups of pressure guide holes C (88) are uniformly distributed on the reversing valve core (64) between the low-pressure grooves (86).

2. The composite impact acceleration drill for coiled tubing of claim 1, wherein: the hydraulic hammer (65) is in abutting connection with the rotating shaft (66) in the clockwise direction; when the reversing valve core (64) is in abutting connection with the hydraulic hammer (65) in the clockwise direction; the high-pressure transmission holes (79) positioned in the first quadrant and the third quadrant on the rotating shaft (66) are communicated with the pressure guide hole B (84) of the hydraulic hammer (65); the second and fourth quadrant high pressure transmission holes (79) and the hydraulic hammer (65) are in a sealing state; two groups of inner low-pressure grooves (78) on the rotating shaft (66) are respectively communicated with a pressure guide hole B (84) of the hydraulic hammer (65); at the moment, two groups of pressure guide holes C (88) of the reversing valve core (64) are respectively communicated with the pressure guide holes A (83) of the hydraulic hammer (65); the two groups of pressure guide holes C (88) are connected with the hydraulic hammer (65) in a sealing way; two groups of low-pressure grooves (86) of the reversing valve core (64) are respectively connected with the inner wall of the hydraulic hammer (65) in a sealing way; the two groups of low-pressure grooves (86) are respectively communicated with a pressure guide hole A (83) of the hydraulic hammer (65); the hydraulic hammer (65) is in interference connection with the rotating shaft (66) in the anticlockwise direction; when the reversing valve core (64) is in abutting connection with the hydraulic hammer (65) in the clockwise direction; the high-pressure transmission holes (79) positioned in the first quadrant and the third quadrant on the rotating shaft (66) are in sealing connection with the hydraulic hammer (65); the second and four-quadrant high-pressure transmission holes (79) are communicated with a pressure guide hole B (84) of the hydraulic hammer (65); two groups of inner low-pressure grooves (78) on the rotating shaft (66) are respectively communicated with a pressure guide hole B (84) of the hydraulic hammer (65); the pressure guide hole B (84) is communicated with an assembling part (85) of the reversing valve core (64); two groups of pressure guide holes C (88) of the reversing valve core (64) are respectively communicated with the pressure guide holes A (83) of the hydraulic hammer (65); the two groups of pressure guide holes C (88) are connected with the hydraulic hammer (65) in a sealing way; two groups of low-pressure grooves (86) of the reversing valve core (64) are respectively connected with the inner wall of the hydraulic hammer (65) in a sealing way; the two groups of low-pressure grooves (86) are respectively communicated with the pressure guide holes A (83) of the hydraulic hammer (65).

3. The composite impact acceleration drill for coiled tubing of claim 2, wherein: the hydraulic hammer (65) is in interference connection with the rotating shaft (66) in the anticlockwise direction; when the reversing valve core (64) is in interference connection with the hydraulic hammer (65) in the anticlockwise direction; the high-pressure transmission holes (79) positioned in the first quadrant and the third quadrant on the rotating shaft (66) are in sealing connection with the hydraulic hammer (65); the second and four-quadrant high-pressure transmission holes (79) are communicated with a pressure guide hole B (84) of the hydraulic hammer (65); two groups of inner low-pressure grooves (78) on the rotating shaft (66) are respectively communicated with a pressure guide hole B (84) of the hydraulic hammer (65); two groups of pressure guide holes C (88) of the reversing valve core (64) are respectively communicated with the pressure guide holes A (83) of the hydraulic hammer (65); the two groups of pressure guide holes C (88) are connected with the hydraulic hammer (65) in a sealing way; two groups of low-pressure grooves (86) of the reversing valve core (64) are respectively connected with the inner wall of the hydraulic hammer (65) in a sealing way; the two groups of low-pressure grooves (86) are respectively communicated with a pressure guide hole A (83) of the hydraulic hammer (65); the hydraulic hammer (65) is in abutting connection with the rotating shaft (66) in the clockwise direction; when the reversing valve core (64) is in interference connection with the hydraulic hammer (65) in the anticlockwise direction; the high-pressure transmission holes (79) positioned in the first quadrant and the third quadrant on the rotating shaft (66) are communicated with the pressure guide hole B (84) of the hydraulic hammer (65); the second and fourth quadrant high pressure transmission holes (79) and the hydraulic hammer (65) are in a sealing state; two groups of inner low-pressure grooves (78) on the rotating shaft (66) are respectively communicated with a pressure guide hole B (84) of the hydraulic hammer (65); the pressure guide hole B (84) is communicated with the assembly part (85); two groups of pressure guide holes C (88) of the reversing valve core (64) are respectively communicated with the pressure guide holes A (83) of the hydraulic hammer (65); the two groups of pressure guide holes C (88) are connected with the hydraulic hammer (65) in a sealing way; two groups of low-pressure grooves (86) of the reversing valve core (64) are respectively connected with the inner wall of the hydraulic hammer (65) in a sealing way; the two groups of low-pressure grooves (86) are respectively communicated with the pressure guide holes A (83) of the hydraulic hammer (65).