CN106948802B

CN106948802B - Vibration damping method for drilling tool

Info

Publication number: CN106948802B
Application number: CN201710129711.2A
Authority: CN
Inventors: 崔龙连; 汪海阁; 张富成; 葛云华; 李洪; 卓鲁斌; 刘力
Original assignee: China National Petroleum Corp; CNPC Drilling Research Institute Co Ltd
Current assignee: China National Petroleum Corp; CNPC Engineering Technology R&D Co Ltd
Priority date: 2017-03-07
Filing date: 2017-03-07
Publication date: 2020-04-10
Anticipated expiration: 2037-03-07
Also published as: CN106948802A

Abstract

The invention discloses a vibration reduction method of a drilling tool, which obtains vibration data of the drilling tool and obtains the current vibration type through a vibration measurement sensor; when the vibration type is axial vibration, comparing the vibration data with a preset first threshold value, and starting an axial damping system when the vibration data is greater than the first threshold value; when the vibration type is circumferential vibration, comparing the vibration data with a preset second threshold value, and starting a circumferential damping system when the vibration data is greater than the second threshold value; when the vibration type is composite vibration, the vibration data is compared with a preset first threshold value and a preset second threshold value, the axial damping system is started when the vibration data is larger than the first threshold value, and the circumferential damping system is started when the vibration data is larger than the second threshold value, so that the axial damping of the drilling tool can be realized, the circumferential damping of the drilling tool can be realized, the damage to the drilling bit caused by the vibration is avoided, the rock breaking efficiency of the drilling bit is improved, and the service life of the tool can be effectively prolonged.

Description

Vibration damping method for drilling tool

Technical Field

The invention relates to the field of petroleum drilling, in particular to a damping method of a drilling tool.

Background

During oil, gas and geological drilling, hard rock layers, gravel rock layers and soft and hard staggered strata are often drilled. Axial vibration, lateral vibration and circumferential vibration of the drill string can be caused by conditions such as uneven bottom of a well, intermittent pressing of drill bit teeth into rock, intermittent crushing of rock, whirling of the drill string around the center of a well hole and the like.

In the case of axial vibration, when the longitudinal vibration frequency of the drill bit is matched with the natural frequency of the longitudinal vibration of the drilling tool, a drill jump phenomenon, namely a resonance phenomenon, is generated. Drill string resonance can cause engineering accidents that can cause premature drill string failure and even eventual well abandonment. The literature reports that annual losses from accidents due to vibration of the downhole drilling tool are in the order of $ 3 billion. The vibration problem of the drill string is one of the main causes of damage to downhole tools and other bottom hole tools and various downhole accidents, and seriously affects the service life of the drilling tool, causes early failure of the drill bit, and seriously affects the service life and the drilling efficiency of the drill bit.

For circumferential vibration, in the normal drilling process of the drill bit, the PDC drill bit continuously eats into the rock under the action of the bit pressure, and the rock is continuously sheared and crushed by the torsion provided by the drill string. When the hardness of stratum rock is high or the drill bit cuts into the stratum too deeply, and the torque at the cutting blade of the drill bit is not enough to break the rock, the drill bit can stop rotating temporarily, and the earth surface drilling disk can rotate continuously at the moment, and the upper drill rod and the lower drill rod have different rotating speeds. Due to the rigidity of the drill pipe, the drill pipe begins to accumulate torque energy. When the torque energy accumulated by the drill rod is larger than the rock breaking energy of the drill bit, the drill bit breaks the rock, the torque energy on the drill string is suddenly released, and the drill bit rotates at a high speed. When the rotation speed of the drill string is reduced to be below a critical value of static friction action, the rotation is stopped, and the phenomenon of sticking-sliding is the phenomenon of stick-sliding vibration, wherein the duration period of the phenomenon is about 1-40 s (seconds). Since the stick-slip vibration process is also a process of energy accumulation and release, the torque fluctuation in the stick-slip vibration process is large, which not only seriously affects the drilling efficiency, but also threatens the drilling safety. For example, when the actual torque is too great, even exceeding the torque limit that the equipment can withstand, drilling may be rendered impossible.

Disclosure of Invention

In view of the above problems, an object of the present invention is to provide a shock absorbing method of a drilling tool for solving at least one of the above problems.

In order to achieve the above object, the present invention provides a method for damping vibration of a drilling tool, comprising the steps of:

acquiring vibration data of the drilling tool through a vibration measuring sensor;

analyzing the obtained vibration data so as to obtain the current vibration type from the vibration data;

when the vibration type is axial vibration, comparing the acquired vibration data with a preset first threshold value, and starting an axial damping system when the vibration data is greater than the first threshold value;

when the vibration type is circumferential vibration, comparing the acquired vibration data with a preset second threshold value, and starting a circumferential damping system when the vibration data is greater than the second threshold value;

when the vibration type is composite vibration, the acquired vibration data are compared with a preset first threshold value, when the vibration data are larger than the first threshold value, an axial damping system is started, the acquired vibration data are compared with a preset second threshold value, and when the vibration data are larger than the second threshold value, a circumferential damping system is started.

Preferably, in the step of acquiring vibration data of the drill by the vibration measuring sensor, the vibration measuring sensor is provided on an outer peripheral wall of the drill.

Preferably, when the vibration type is axial vibration, the step of comparing the acquired vibration data with a preset first threshold value, and when the vibration data is greater than the first threshold value, the step of starting the axial damping system further includes:

after the axial damping system is started, vibration data of the drilling tool are obtained through the vibration measuring sensor; and comparing the latest acquired vibration data with a preset first threshold value, and closing the axial damping system when the latest acquired vibration data is smaller than the first threshold value.

Preferably, when the vibration type is circumferential vibration, the step of comparing the acquired vibration data with a preset second threshold value, and when the vibration data is greater than the second threshold value, the step of starting the circumferential damping system further includes:

after the circumferential damping system is started, vibration data of the drilling tool are obtained through a vibration measuring sensor;

and comparing the latest acquired vibration data with a preset second threshold value, and closing the circumferential damping system when the latest acquired vibration data is smaller than the first threshold value.

Preferably, in the step of acquiring vibration data of the drilling tool by the vibration measuring sensor, the vibration measuring sensor acquires the vibration data of the drilling tool every 1 second or 2 seconds.

Preferably, the circumferential damping system and the axial damping system are hydraulic devices.

Preferably, the circumferential shock absorbing system comprises:

a first outer tube;

the reciprocating rotating mechanism is arranged in the first outer pipe and comprises a reciprocating impact device and a reciprocating cylinder sleeved outside the reciprocating impact device;

at least two pressure chambers which are isolated from each other are formed between the reciprocating impact device and the reciprocating cylinder, and the volume of each pressure chamber is changed along with the change of the volume of liquid in the pressure chambers;

the reciprocating impact device is provided with liquid inlet through holes which can be respectively communicated with the pressure chambers;

the reciprocating cylinder is provided with a first liquid discharge port, the first outer pipe is provided with a second liquid discharge port which can be communicated with the first liquid discharge port, and each pressure chamber can be sequentially communicated with the first liquid discharge port and the second liquid discharge port to form a liquid discharge flow channel, so that the reciprocating impact device can rotate in the reciprocating cylinder in a reciprocating manner in the circumferential direction.

Preferably, the axial damping system comprises:

a second outer tube connectable to the first outer tube;

a pressure conducting bore disposed in a wall of the second outer tube;

the damping balance part is sleeved in the second outer pipe in a sliding manner and is subjected to internal pressure of the drilling fluid acting on the upper end surface of the second outer pipe,

the damping balance part is provided with a convex part which is positioned above the pressure conduction hole, the outer wall of the convex part is attached to the inner wall of the second outer pipe, and the lower end surface of the convex part is used for bearing the external pressure input from the pressure conduction hole;

the reducing mechanism is arranged in the damping balance part and provided with a first flow channel penetrating through the second outer pipe in the length direction, the control device is electrically connected with the reducing mechanism and can control the reducing mechanism to change the inner diameter of the first flow channel so as to control the inner pressure.

Preferably, the circumferential damping system is arranged above the axial damping system.

Preferably, the vibration measuring sensor is arranged above the circumferential damping system and the axial damping system.

The method comprises the steps of firstly collecting vibration data of a drilling tool at a preset sampling frequency through a vibration measuring sensor, then processing the vibration data, and sending out the vibration data in a vibration signal mode. Wherein the vibration signal comprises a vibration type and a vibration intensity. The control device can receive the vibration signal sent by the vibration measuring sensor and analyze and compare the vibration signal. The control device first determines whether the vibration signal is axial vibration or circumferential vibration. When the vibration is axial vibration, the control device compares the vibration signal with a first preset threshold value. When the first threshold value is exceeded, the control device starts the axial damping system. When the vibration is a circumferential vibration, the control device compares the vibration signal with a second threshold value. When the value is larger than the second threshold value, the control device starts the circumferential damping system. When the vibration is axial vibration and circumferential vibration at the same time, the control device compares the vibration signal with the first threshold value and the second threshold value at the same time. When being greater than first threshold value and/or second threshold value, controlling means starts axial shock mitigation system and/or circumference shock mitigation system simultaneously to the axial shock attenuation that both carried out the drilling tool can carry out the shock attenuation of circumference to the drilling tool again, has avoided because vibrations and to the destruction of drill bit, improves the broken rock efficiency of drill bit, can effectively improve the instrument life-span again.

Drawings

FIG. 1 is a flow chart of a method of damping vibration of a drilling tool of the present application;

FIG. 2 is a schematic structural view of a composite vibration reducing tool according to an embodiment of the present application;

FIG. 3 is a schematic cross-sectional view of a third housing of a composite vibration dampening tool of an embodiment of the present application;

FIG. 4 is a cross-sectional schematic view of a shuttle cylinder of a circumferential dampening system of a composite dampening tool of an embodiment of the present application;

FIG. 5 is a schematic cross-sectional view of a reciprocating hammer of a circumferential dampening system of a composite dampening tool according to an embodiment of the present disclosure;

FIG. 6 is a schematic view of a partial structure of a circumferential dampening system of a composite dampening tool according to an embodiment of the present disclosure;

FIG. 7 is a schematic diagram illustrating a clockwise impact motion state of a circumferential damping system of a composite damping tool according to an embodiment of the present disclosure;

FIG. 8 is a schematic diagram illustrating a state of counterclockwise impact motion of a circumferential damping system of a composite damping tool according to an embodiment of the present disclosure;

FIG. 9 is a schematic view of the shock absorbing counter balance of FIG. 2 engaged with the outer tube;

FIG. 10A is a schematic structural diagram of the electromagnetic variable diameter valve in a non-diameter-reducing state;

FIG. 10B is a schematic structural diagram of a diameter-reduced state of the electromagnetic variable diameter valve;

FIG. 11A is a schematic view of the pressure applied to the damping balance portion when the electromagnetic reducing valve is not in a diameter reduction state;

FIG. 11B is a force-receiving schematic diagram of the shock-absorbing balance portion of FIG. 11A;

FIG. 12A is a schematic view of the pressure applied to the damping balance portion in the diameter-reduced state of the electromagnetic reducing valve;

FIG. 12B is a force-receiving schematic diagram of the shock-absorbing balance portion in FIG. 12A;

FIG. 13A is a schematic view of the axial damping system in a non-diameter-reducing state of the electromagnetic reducing valve;

FIG. 13B is a schematic view of the axial damping system in a reduced diameter state of the electromagnetic reducing valve;

FIG. 14 is a schematic diagram of the electrical connections of the components in the composite vibration dampening tool.

Detailed Description

In order to make those skilled in the art better understand the technical solutions in the present application, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

The invention provides a vibration reduction method of a drilling tool, which comprises the following steps as shown in figure 1:

s1: acquiring vibration data of the drilling tool through a vibration measuring sensor;

in this step, the vibration measuring sensor may be provided on the outer peripheral wall of the drill. The vibration measuring sensor can continuously detect the vibration condition of the drilling tool. Specifically, the vibration measuring sensor can acquire vibration data of the drilling tool every 1 second or 2 seconds.

S2: analyzing the obtained vibration data, so as to obtain the current vibration type from the vibration data;

in this step, the vibration types may be roughly classified into axial vibration and circumferential vibration. The waveforms and the intensities generated by the axial vibration and the axial vibration are different, so that the control device needs to analyze and compare vibration data, determine the intensities of the vibrations of all types, then respectively compare the intensities, and further determine whether the intensities of all the vibrations reach the preset intensities, thereby controlling the opening and closing of the axial damping system and the circumferential damping system.

S3: when the vibration type is axial vibration, comparing the acquired vibration data with a preset first threshold value, and starting an axial damping system when the vibration data is greater than the first threshold value; when the vibration type is circumferential vibration, comparing the acquired vibration data with a preset second threshold value, and starting a circumferential damping system when the vibration data is greater than the second threshold value; when the vibration type is composite vibration, the acquired vibration data are compared with a preset first threshold value, when the vibration data are larger than the first threshold value, the axial damping system is started, the acquired vibration data are compared with a preset second threshold value, and when the vibration data are larger than the second threshold value, the circumferential damping system is started.

Wherein the first threshold value and the second threshold value can be determined according to the type of the drilling tool and the actual working condition and environment when drilling. The values of the first threshold and the second threshold may be set before drilling, and the device is activated when the vibration data is greater than the first threshold or the second threshold.

The step can also comprise:

after the axial damping system is started, acquiring vibration data of the drilling tool through a vibration measuring sensor; comparing the latest acquired vibration data with a preset first threshold value, and closing the axial damping system when the latest acquired vibration data is smaller than the first threshold value;

after the circumferential damping system is started, vibration data of the drilling tool are obtained through a vibration measuring sensor; and comparing the latest acquired vibration data with a preset second threshold, and closing the circumferential damping system when the latest acquired vibration data is smaller than the first threshold.

The circumferential damping system and the axial damping system are hydraulic devices. Wherein, circumference shock mitigation system includes: a first outer tube; the reciprocating rotating mechanism is arranged in the first outer pipe and comprises a reciprocating impact device and a reciprocating cylinder sleeved outside the reciprocating impact device; at least two pressure chambers which are isolated from each other are formed between the reciprocating impact device and the reciprocating cylinder, and the volume of each pressure chamber is changed along with the change of the volume of liquid in the pressure chambers; the reciprocating impact device is provided with liquid inlet through holes which can be respectively communicated with each pressure chamber; the reciprocating cylinder is provided with a first liquid discharge port, the first outer pipe is provided with a second liquid discharge port which can be communicated with the first liquid discharge port, and each pressure chamber can be sequentially communicated with the first liquid discharge port and the second liquid discharge port to form a liquid discharge flow channel, so that the reciprocating impact device can rotate in the reciprocating cylinder in a reciprocating manner in a circumferential direction, and impact force generated by circumferential movement is compensated.

Referring to fig. 2 and 14, the composite damping tool can be connected with a drilling tool to damp the drilling tool. This compound shock attenuation instrument includes: the vibration detection device can generate a vibration signal according to the vibration generated by the drilling tool; the axial damping system is used for compensating the axial acting force applied to the drilling tool; the circumferential damping system is used for compensating circumferential acting force applied to the drilling tool; the control device 205, the control device 205 is electrically connected with the vibration detection device, the axial damping system and the circumferential damping system respectively; the control device is used for controlling the axial damping system and the circumferential damping system according to the vibration signals.

The vibration detection device firstly collects vibration data of the drilling tool at a preset sampling frequency, then processes the vibration data and sends out the vibration data in a vibration signal mode. Wherein the vibration signal comprises a vibration type and a vibration intensity. The control device 205 can receive the vibration signal from the vibration detection device and analyze and compare the vibration signal. The control device 205 first determines whether the vibration signal is axial vibration or circumferential vibration. When the vibration is an axial vibration, the control device 205 compares the vibration signal with a first preset threshold. When greater than the first threshold, the control device 205 activates the axial damping system. When the vibration is a circumferential vibration, the control device 205 compares the vibration signal with a second threshold value. When greater than the second threshold, the control device 205 activates the circumferential damping system. When the vibration is axial vibration and circumferential vibration at the same time, the control device 205 compares the vibration signal with the first threshold and the second threshold at the same time. When being greater than first threshold value and/or second threshold value, controlling means 205 starts axial shock mitigation system and/or circumference shock mitigation system simultaneously to both axial shock attenuation that has gone on the drilling tool can carry out the shock attenuation of circumference to the drilling tool again, avoided because vibrations and to the destruction of drill bit, improve the broken rock efficiency of drill bit, can effectively improve tool life again.

In the embodiment, the power supply device is used for supplying power to the composite damping tool to ensure the downhole power utilization of the tool. For downhole tool power, common voltage specifications include: 12V and 36V. The power supply device may be powered by a battery, or may be powered by a turbine generator, or may be powered by other forms, and the present application is not limited in particular.

Referring to fig. 2, the power supply device may include: a third outer pipe 101, a power supply cavity sealing cover 102, a power supply cavity 103, a power supply 105, a power supply outlet 106 with a seal, and a power supply cable 107, wherein the power supply device is further provided with a through flow hole 104 for flowing drilling fluid. The third outer tube 101 may have a hollow cylindrical shape, and the hollow portion is a through hole. Specifically, the inner side of the upper end of the third outer tube 101 may be provided with an internal thread for connecting with an upper drilling tool, the outer side of the lower end may be provided with an external thread for connecting with a vibration monitoring system, and a limiting step for limiting the power supply cavity 103 is arranged inside the outer tube.

The flowthrough bore 104 is used to circulate drilling fluid. Specifically, the overflowing hole 104 may be disposed on the power supply cavity 103, or on the third outer tube 101, or formed by a gap between the power supply cavity 103 and the third outer tube 101, or may be disposed in another manner, which is not specifically limited herein. In addition, the number of the overflowing holes 104 may be one or more, and the present application is not limited in particular, and when the number of the overflowing holes 104 is more, the overflowing holes may be uniformly arranged along the circumferential direction of the third outer pipe 101.

Furthermore, flange rings for centralizing and positioning can be arranged at the upper end and the lower end of the power supply cavity 103. An overflow aperture 104 is provided in the flange ring. The flange ring abuts against the limit step, and the flange ring is in clearance fit with the third outer pipe 101. When the drilling fluid in the well is circulated in the drilling device, it can be circulated through the flowbore 104 and the gap between the flange ring and the third outer tube 101 when passing through the current supply means.

The power supply cavity 103 and power supply cavity seal cover 102 cooperate to provide a power supply 105 to isolate the power supply 105 from the drilling fluid. The shape and size of the power supply cavity 103 may be determined according to the shape and size of the power supply 105, and the present application is not limited thereto. In addition, the power supply cavity 103 and the power supply cavity sealing cover 102 can be detachably connected to facilitate the disassembly and assembly of the power supply 105. For example, the power supply chamber sealing cover 102 may be a plug with certain elasticity, which is disposed at the opening end of the power supply chamber 103 by means of interference fit. In addition, a sealed power outlet 106 may be provided at a lower portion of the power chamber 103, and a power supply cable 107 may be fed to each device through the sealed power outlet 106.

In this embodiment, the vibration detection device is used to monitor and process downhole drilling tool vibrations in real time. The vibration detection device can detect the vibration generated by the drilling tool and send out a vibration signal, wherein the vibration signal comprises the vibration type and the vibration strength. The control device 205 can receive the vibration signal from the vibration system and send out the first execution signal or the second execution signal according to the type and intensity of the vibration signal. The axial damping system can receive a first execution signal sent by the judging system and is started. And the circumferential damping system can receive a second execution signal sent by the judgment system and is started.

In this embodiment, the vibration detection device may include: a fourth outer tube 201, a vibration measuring sensor 202 disposed on the fourth outer tube 201. The vibration measurement sensor 202 may be a sensor unit, among others. The sensor unit can detect vibration data of the drilling tool in real time. The vibration measuring sensor 202 is powered by a power supply.

In the present embodiment, the control device 205 may be provided in the fourth outer tube 201. The control device 205 is electrically connected to the vibration detection device. The vibration detection device can detect the vibration generated by the drilling tool and send out the vibration signal. The control device 205 can receive the vibration signal from the vibration system and send out the first execution signal or the second execution signal according to the type and intensity of the vibration signal. The first execution signal and the second execution signal can respectively start the circumferential damping system and the axial damping system.

The fourth outer tube 201 may be a hollow cylinder, the hollow portion is a through hole, and joints, i.e., an upper joint and a lower joint, may be disposed at upper and lower ends of the hollow portion. The inner side of the upper joint may be provided with an internal thread for coupling with the third outer tube 101; the outer side of the lower joint may be provided with an external thread for connection with an axial damping system or a circumferential damping system. Of course, the third outer tube 101 and the fourth outer tube 201 may be a single housing; in addition, when two housings are provided, they may be connected by other connection methods, and the present application is not limited to this. A vibration measuring sensor 202, a control device 205 and a power supply cable 107 are arranged in the fourth outer tube 201.

Specifically, the outer wall of the fourth outer tube 201 may be provided with a first groove and a detection device sealing gland 203 matched with the first groove. The second groove and a control device matched with the second groove seal the gland 204. The vibration measuring sensor 202 is arranged in the first groove and is sealed by a detection device sealing gland 203; the control device 205 is arranged in the second groove and is sealed by the control device gland 204.

The vibration measuring sensor 202 is used to obtain a vibration signal of the drilling tool, and the specific form and installation manner thereof are not limited in this application. For example, the vibration measuring sensor 202 may be mounted on the fourth outer tube 201 by a screw thread. Further, the vibration measuring sensor 202 is sealed by a sealing gland 203 of the detection device, so that drilling fluid in the well is prevented from entering the vibration measuring sensor 202 and affecting the normal operation of the vibration measuring sensor. Of course, if the vibration measuring sensor 202 has a waterproof function, the detection device sealing cover 203 may be omitted.

The control device 205 may be electrically connected to the vibration measuring sensor 202, and may receive a vibration signal from the vibration measuring sensor 202, compare the processed vibration signal with a preset vibration threshold, and start the axial damping system or the circumferential damping system according to the type of vibration when the detected value is greater than the preset vibration threshold. The form and mounting manner of the control device 205 and the like in the present application are not particularly limited. For example, the control device 205 may be mounted on the fourth outer tube 201. Further, the control device gland 204 seals the control device 205 to prevent well drilling fluid from entering the control device 205. Of course, the control device gland 204 may be omitted if the control device 205 has a waterproof function.

The fourth outer tube 201 may be provided with a power supply seal hole, and the power supply cable 107 connected to the power supply 105 supplies power to the vibration measuring sensor 202 and the control device 205 through the power supply seal hole of the fourth outer tube 201.

In this embodiment, the circumferential damping system comprises: a first outer tube 301; and the reciprocating rotating mechanism is arranged in the first outer pipe 301, and comprises a reciprocating impact device 3011 and a reciprocating cylinder 305 sleeved outside the reciprocating impact device 3011. At least two pressure chambers 30502 isolated from each other are formed between the reciprocating impact device 3011 and the reciprocating cylinder 3011. Wherein the volume of each pressure chamber 30502 varies with the volume of liquid within the pressure chamber 30502. The reciprocating impact device 3011 can move in the reciprocating cylinder 305 by increasing the volume of one pressure chamber 30502 and decreasing the volume of the other pressure chamber 30502.

The reciprocating impact device 3011 may be provided with a liquid inlet hole 307. The liquid inlet through holes 307 can be respectively communicated with the pressure chambers 30502. The reciprocating cylinder 3011 is provided with at least two first drain ports 309. The first outer tube 301 is provided with a second drain port 3010 that can communicate with any of the first drain ports 309. Each pressure chamber 30502 can be sequentially communicated with the first liquid discharge port 309 and the second liquid discharge port 3010 to form a liquid discharge channel, so that the reciprocating impact device 3011 can rotate back and forth in the reciprocating cylinder 305 in the circumferential direction. Further, the circumferential damping system can further comprise a sheath, a longitudinal compression spring 303, a sealing gland 304, a first solenoid valve 306 and a second solenoid valve 308.

The first outer tube 301 has opposite upper and lower ends, the lower end of which may be connected to a bit sub 3012 by a force transfer mechanism. The bit sub 3012 is used to connect a drill bit to transmit torque generated by the circumferential reciprocating rotation to the drill bit. Of course, the lower end of the first outer tube 301 may also be connected to an axial damping system or a power supply. For example, the first outer tube 301 may be connected to the second outer tube 401. The operator can adjust the installation sequence of each device according to actual operation requirements. As a whole, the first outer tube 301 may have a hollow cylindrical shape, a hollow portion of which is a through hole. Further, the through hole of the first outer tube 301 is a stepped through hole with a variable inner diameter.

When the lower end of the first outer tube 301 may be connected to the bit connector 3012 through a force-transfer mechanism, the upper portion of the first outer tube 301 may be provided with internal threads for connection with the lower end of the fourth outer tube 201; the lower part of the device can be provided with a force transmission piece for transmitting torque, and particularly, the force transmission piece can be a spline. Correspondingly, the bit sub 3012 may be provided with a key slot that mates with a spline, the spline and the key slot mating to form a force transfer mechanism. Of course, the form of the force transmission mechanism is not limited to the form of the spline and the key slot, and other forms capable of transmitting torque may be adopted, and other modifications are possible for those skilled in the art in light of the technical spirit of the present application, but the present application is intended to cover the scope of the present application as long as the functions and effects achieved by the force transmission mechanism are the same as or similar to those of the present application.

A second drain port 3010 may be provided on the side wall of the first outer tube 301 for draining drilling fluid to and from the shuttle cylinder 305. Specifically, the number of the second liquid discharge ports 3010 may be an even number, for example, two, four, six, etc., and the present application is not limited thereto. The second liquid discharge ports 3010 may be arranged symmetrically along the axial direction. Further, the first outer tube 301 is provided with an annular liquid discharge groove 30101 for communicating with the second liquid discharge port 3010. When the reciprocating cylinder 305 performs reciprocating impact motion, the plurality of first discharge ports 309 may rotate on the same circumference, and in this embodiment, they are connected together by using the annular discharge groove 30101, and thus can be used to transmit high and low pressures.

Shuttle cylinder 305 may be a hollow cylinder. The shuttle cylinder 305 may include a shuttle cylinder body having a hollow cylindrical shape; a first drain port 309 provided in the reciprocating cylinder body; two first fan-shaped protrusions are oppositely arranged on the inner side wall of the reciprocating cylinder body. Specifically, the shuttle cylinder 305 may be a "T" shaped cylinder with a large upper end diameter and a small lower end diameter as a whole. Specifically, the inner hole at the upper end of the reciprocating cylinder 305 is in a shape formed by four circular arcs and four straight line segments, the four circular arcs are two circular arcs with different diameters, and the two large-diameter circular arcs and the four straight line segments form two symmetrical first fan-shaped bulges. The inner hole of the lower portion of the shuttle cylinder 305 is a through hole, and the diameter of the through hole is equal to or smaller than the diameter of the upper small-diameter circular arc. The upper large diameter section of the shuttle cylinder 305 is provided with a first drain 309 for draining drilling fluid from the shuttle cylinder 305. The number of the first liquid discharge ports 309 may be an even number.

The reciprocating impact device 3011 is cylindrical. The shuttle impact device 3011 includes: the reciprocating impact device body is a hollow cylinder; a liquid inlet through hole 307 arranged on the reciprocating impact device body; two fan-shaped archs of second, the fan-shaped protruding setting back of the body of second is on the lateral wall that comes and goes the impact device body, first fan-shaped protruding and the fan-shaped protruding looks adaptation of second to make come and go the impact device and come and go and be formed with two at least pressure chamber between the impact cylinder. The second fan-shaped bulge consists of four circular arcs and four straight line segments. The two large-diameter section circular arcs and the four sections of straight lines form two symmetrical second fan-shaped bulges. The shuttle 3011 is mounted in the shuttle cylinder 305, and the sector-shaped protrusion of the shuttle 3011 is in the sector-shaped space of the shuttle cylinder 305. The circular arc angle corresponding to the sector-shaped projection of the reciprocating impact device 3011 is smaller than the circular arc angle corresponding to the sector-shaped space of the reciprocating cylinder 305. So that at least two pressure chambers 30502 isolated from each other can be formed between the reciprocating impact device 3011 and the reciprocating cylinder 3011. The diameter of the circular arc of the large-diameter section at the lower part of the reciprocating impact device 3011 is the same as the diameter of the circular arc of the large diameter of the inner hole at the upper part of the reciprocating impact cylinder 305, and the diameter of the circular arc of the small-diameter section at the lower part of the reciprocating impact device 3011 is the same as the diameter of the circular arc of the small diameter of the inner hole at the upper part of.

The shuttle impact device 3011 may also include a longitudinal compression spring 303, which may be used to provide a restoring force to the first and second solenoid valves 306, 308 abutting thereto. Specifically, the longitudinal compression spring 303 may include a first longitudinal compression spring and a second longitudinal compression spring. The first longitudinal pressure spring is used for being matched with the first electromagnetic valve 306; the second longitudinal compression spring is used for the second longitudinal compression spring matched with the second electromagnetic valve 308.

The reciprocating impact device 3011 is provided with a liquid inlet through hole 307 for flowing drilling liquid. When the liquid inlet through hole 307 communicates with the annular space, a liquid inlet passage is formed. Specifically, the number of the liquid inlet through holes 307 may be even.

The first electromagnetic valve 306 can be in a circular arc strip shape and is matched with the longitudinal pressure spring 303 for use, and when the first electromagnetic valve 306 is electrified, the first electromagnetic valve 306 is pushed upwards to open the liquid inlet through hole 307. The sheath can be cylindrical and is arranged at the upper end of an inner hole of the reciprocating impact device 3011 and used for positioning the longitudinal pressure spring 303 and the first electromagnetic valve 306.

The seal gland 304 is used to form a seal cavity with the reciprocating cylinder 305 and the reciprocating impact device 3011, and the reciprocating impact device 3011 is driven to perform circumferential impact motion under the action of drilling hydraulic pressure. Specifically, the gland 304 may have a circular ring shape, and has an outer diameter equal to the outer diameter of the upper portion of the reciprocating cylinder 305 and an inner diameter equal to the outer diameter of the upper cylindrical section of the reciprocating impact device 3011. The shuttle impact cylinder 305 is mounted at the inner bore step of the first outer tube 301, the inner bore step of the first outer tube 301 providing support for the shuttle impact cylinder 305.

A second longitudinal compression spring and a second solenoid valve 308 are provided between the reciprocation cylinder 305 and the first outer tube 301. When the second solenoid valve 308 is energized, the second solenoid valve 308 moves downward, and opens the second drain port 3010 and the first drain port 309, thereby draining the drilling fluid in the reciprocating cylinder 305. The lower portion of the reciprocating impact cylinder 305 is connected to the bit sub 3012 by threads, and the splines on the lower portion of the outer housing 301 of the two types of connected circumferential damping systems are matched with the splines on the large-diameter section of the upper portion of the bit sub 3012, so as to transmit the torque of the drill string and the additional reciprocating impact torque generated by the reciprocating impact cylinder 305.

When the circumferential damping system is not activated, the first outer tube 301 is engaged with the bit sub 312 through the lower spline, transmitting the upper tool torque to the bit for breaking rock. After the circumferential damping system is started, the spline is matched to transmit the torque of the upper drilling tool for rock breaking of the drill bit on the one hand, and meanwhile, the periodic impact torque of the reciprocating motion cylinder 305 is transmitted to reduce circumferential stick-slip vibration of the drilling tool, so that the rock breaking efficiency of the drill bit is improved, and the drill bit is protected.

When the circumferential damping system starts to work, the first electromagnetic valve 306 corresponding to the liquid inlet through hole 307 moves upwards, the liquid inlet through hole 307 is opened, and high-pressure drilling fluid in the drilling tool can enter a pressure chamber 30502 formed between the reciprocating cylinder 305 and the reciprocating impact device 3011 through the liquid inlet through hole 307. Specifically, when the number of the pressure chambers 30502 is two, high-pressure drilling fluid may enter one of the pressure chambers 30502. When there are four pressure chambers 30502, high pressure drilling fluid can enter the two opposing chambers. At the same time, the second solenoid valve 308 of the reciprocation cylinder 305 moves downward, opening the first drain port 309, so that the first drain port 309 communicates with the second drain port 3010.

When high-pressure drilling fluid enters the reciprocating cylinder 305 to form a sector-shaped sealed space (a pressure chamber 30502) with the reciprocating impact device 3011 and the sealing gland, the high-pressure drilling fluid pushes the reciprocating impact device 3011 to move, when the reciprocating impact device 3011 moves to a direction dead point, the reciprocating impact device 3011 impacts the reciprocating cylinder 305, under the action of impact force, the reciprocating cylinder 305 moves and is transmitted to a drill bit through the lower drill bit connector 3012, at the moment, the now-opened liquid inlet through hole 307 and the first liquid outlet 309 are closed through the first electromagnetic valve 306 and the second electromagnetic valve 308, and the other liquid inlet through hole 307 and the first liquid outlet 309 are opened. High pressure drilling fluid enters the pressure chamber 30502 that is not entered and does not enter the pressure chamber 30502 that is already entered. The high-pressure drilling fluid further pushes the reciprocating impact device 3011 to move reversely, when the reciprocating impact device 3011 moves to a reverse dead point, the opened liquid inlet through hole 307 and the first liquid outlet 309 are closed, and the other liquid inlet through hole 307 and the first liquid outlet 309 are opened. The reciprocating impact device 3011 performs reciprocating impact motion, and the reciprocating hydraulic cylinder 305 performs reciprocating motion under the impact action of the reciprocating impact device 3011 and transmits the reciprocating motion to the drill bit through the lower spline. The reciprocating movement of the drill bit can effectively reduce the circumferential stick-slip vibration of the drill bit of the drilling tool, improve the rock breaking efficiency of the drill bit and protect the drill bit.

In a particular embodiment, the circumferential damping system comprises: the drill bit comprises a first outer pipe 301, a sheath, a longitudinal pressure spring 303, a sealing gland 304, a reciprocating cylinder 305, a first solenoid valve 306, a second solenoid valve 308, a reciprocating impact device 3011 and a drill bit 3012. The first outer tube 301 is a hollow cylinder, the hollow part is a step through hole, the upper part of the hollow part is provided with a connecting thread for connecting with the lower part of the fourth outer tube 201 through a thread, and the lower part of the hollow part is provided with a spline for transmitting torque. As shown in fig. 3, the first outer pipe 301 has 2 symmetrical second liquid discharge ports 3010 for discharging the drilling fluid in the return cylinder 305 to the annulus. The two liquid discharge ports are communicated through an annular liquid discharge groove 30101.

The shuttle cylinder 305 is a hollow "T" shaped cylinder with a large upper end diameter and a small lower end diameter. As shown in fig. 4, the inner bore of the upper end of the shuttle cylinder 305 is in the shape of a four-segment circular arc and four straight segments. The four sections of circular arcs comprise two circular arcs with large diameters and two circular arcs with small diameters. The two large-diameter circular arc sections and the four straight line sections form two symmetrical fan-shaped spaces, and the angle of the fan-shaped spaces corresponding to circular arcs is 30-175 degrees. The inner hole of the lower part of the reciprocating cylinder 305 is a through hole, and the diameter of the through hole is equal to or smaller than that of the circular arc with the small diameter of the upper part, and is used for forming a drilling fluid circulation channel. The upper large diameter section of the shuttle cylinder 305 has four first fluid discharge ports 309 for discharging drilling fluid from the shuttle cylinder. The first drainage ports, respectively 309A and 309B, of fig. 4, are identically numbered with the same opening and closing steps during operation of the circumferential damping system. A second solenoid valve locking groove 30501 is formed on a side wall of the reciprocating cylinder 305, and is used for positioning and mounting the second solenoid valve 308 and the longitudinal compression spring 303. Specifically, the second solenoid slot 30501 may be located opposite to the first drain port 309 in the circumferential direction. Specifically, the number of the second solenoid valve slots 30501 may be the same as the number of the second solenoid valves 308 and the number of the first drain ports 309, and the positions of the second solenoid valves and the first drain ports are matched. When the number of the first liquid discharge ports 309 is four, as shown in fig. 4, the second solenoid valve slot 30501 is axially symmetric 30501A and 30501B in the set. When energized, the second solenoid valve 308 moves downward to open the first drain port 309.

Referring to fig. 5, the reciprocating impact device 3011 may be cylindrical and may be composed of four circular arcs and four straight segments. At least two pressure chambers 30502 may be formed between the shuttle 3011 and the shuttle cylinder 305. The pressure chambers 30502 can be two or four when the shuttle 3011 is moved relative to the shuttle cylinder 305.

Wherein, two large diameter section circular arcs and four sections straight lines form two symmetrical fan-shaped convex blocks, the angle of the circular arc corresponding to the fan shape can be 30-150 degrees, and the angle of the circular arc corresponding to the fan-shaped bulge of the reciprocating impact device 3011 is smaller than the angle of the circular arc corresponding to the fan-shaped space of the reciprocating cylinder 305.

The shuttle percussion device 3011 has four inlet holes 307, as shown in fig. 6, which are respectively marked as 307A and 307B, for providing a drilling fluid inlet channel, and the inlet holes 307 of the shuttle percussion device with the same mark have the same opening and closing steps when the circumferential damping system works.

The first electromagnetic valve 306 can be in an arc-shaped strip shape, is matched with the longitudinal pressure spring 303 for use, and is installed in first electromagnetic valve clamping grooves (301101a, 301101B), wherein the number of the first electromagnetic valve clamping grooves (301101a, 301101B) is the same as that of the first electromagnetic valve 306 and the liquid inlet through hole 307, and the positions of the first electromagnetic valve clamping grooves are matched with those of the liquid inlet through hole 307. When the liquid inlet through holes 307 are four conjugated, as shown in fig. 5, the first solenoid valve slots are the first solenoid valve slot 301101a and the first solenoid valve slot 301101B that are axially symmetric in the group. When the power is on, the first electromagnetic valve 306 pushes upwards to open the liquid inlet through hole 307.

The sheath may be cylindrical and is mounted on the upper end of the inner bore of the reciprocating impact device 3011 for positioning the longitudinal compression spring 303 and the first solenoid valve 306.

The gland 304 may be circular, and has an outer diameter equal to the outer diameter of the upper portion of the reciprocating cylinder 305 and an inner diameter equal to the outer diameter of the upper cylindrical section of the reciprocating impact device 3011.

The lower portion of the shuttle cylinder 305 is threadedly connected to the bit sub 312, and the splines on the lower portion of the outer housing 301 of the circumferential damping system after connection are engaged with the splines on the upper large diameter section of the bit sub 312 for transferring the torque of the drill string and the additional shuttle torque generated by the shuttle cylinder 305.

The shuttle cylinder 305 is mounted at the inner bore step of the first outer tube 301, and the inner bore step of the first outer tube 301 provides support for the shuttle cylinder 305 (shown in figure 2). As shown in fig. 6, the reciprocating impact device 3011 is installed in the reciprocating cylinder 305, the sector-shaped protrusion of the reciprocating impact device 3011 is located in the sector-shaped space of the reciprocating cylinder 305, the circular arc diameter of the large-diameter section of the lower portion of the reciprocating impact device 3011 is the same as the circular arc diameter of the large diameter section of the inner hole of the upper portion of the reciprocating cylinder 305, and the circular arc diameter of the small-diameter section of the lower portion of the reciprocating impact device 3011 is the same as the circular arc diameter of the small diameter section of the inner hole of the.

The function of the gland 304 is to allow the shuttle cylinder 305 and shuttle ram 3011 to form a pressure chamber 30502. Specifically, the gland 304 may be disposed at the upper end of the reciprocating impact cylinder 305 and sleeved outside the reciprocating impact device 3011.

As shown in fig. 7 and 8, when the circumferential damping system rotates clockwise to impact, and the circumferential damping system starts to operate, the 2 liquid inlet through holes 307B move upward corresponding to the first electromagnetic valve 306 in the first electromagnetic valve slot 301101B, and open the 2 liquid inlet through holes 307B, and meanwhile, the second electromagnetic valve 308 in the second electromagnetic valve slot 30501B corresponding to the low-pressure liquid outlet 309B of the 2 reciprocating cylinders moves downward, and opens the low-pressure liquid outlet 309B of the 2 reciprocating cylinders. High-pressure drilling fluid in the drilling tool enters the reciprocating cylinder 305 through the 2 liquid inlet through holes 307B to form a sector-shaped sealed space with the reciprocating impact device 3011 and the sealing gland 304, and at the moment, the pressure chamber 30502 is connected with the low-pressure annular drilling fluid through the annular fluid discharge groove 30101 and the second fluid discharge port 3010. Because the drilling fluid pressure in the drilling tool is higher than the annulus drilling fluid pressure, and pressure difference exists between the two surfaces of the reciprocating impact device 3011, the reciprocating impact device 3011 rotates clockwise under the pushing of the high-pressure drilling fluid. When the reciprocating impact device 3011 moves to a dead point in one direction, the reciprocating impact device 3011 impacts the reciprocating cylinder 305, and the reciprocating cylinder 305 is moved by the impact force and is transmitted to the bit through the lower bit sub 3012. In addition, when the return hammer 311 moves to one direction dead point, the 2 liquid inlet through holes 307B and the 2 first drain ports 309B, which have been opened now, are closed by the movement of the first solenoid valve 306, the second solenoid valve 308. As shown in fig. 8 and 9, the other 2 liquid inlet through holes 307A and the 2 first liquid outlet ports 309A are opened. The high-pressure drilling fluid reversely pushes the reciprocating impact device 3011 to move anticlockwise, when the reciprocating impact device 3011 moves to a reverse dead point, the opened 2 liquid inlet through

holes

307A and 2 first liquid discharge ports 309A are closed, and the other 2 liquid inlet through

holes

307B and 2 first liquid discharge ports 309B are opened. The reciprocating impact device 3011 performs reciprocating impact motion in the reciprocating cylinder 305 (shown in fig. 7 and 8). The reciprocating hydraulic cylinder 305 reciprocates by the impact of the reciprocating impact device 3011 and is transmitted to the drill bit through the lower spline. The reciprocating movement of the drill bit can effectively reduce the circumferential stick-slip vibration of the drill bit of the drilling tool, improve the rock breaking efficiency of the drill bit and protect the drill bit.

In the embodiment, the power supply device provides power for the composite damping tool, and downhole power utilization of the tool is guaranteed. The power supply device includes: a third outer tube 101, a power supply cavity sealing cover 102, a power supply cavity 103, an overflowing hole 104, a power supply 105, a power supply outlet 106 with a seal and a power supply cable 107. The third outer tube 101 is a hollow cylinder, and the hollow portion is a step through hole. The upper part of the third outer pipe 101 is connected to the drill by means of screw threads, and the lower part thereof can also be connected to the fourth outer pipe 201 by means of screw threads. The upper end and the lower end of the power supply cavity 103 are provided with righting and positioning flange rings, and the flange rings are provided with overflowing holes 104. The end face of the lower flange corresponding to the power supply cavity 103 is arranged on a step hole in the third outer tube 101, and the outer diameter of the flange ring is in clearance fit with the inner hole of the third outer tube 101. The power supply 105 is arranged in the power supply cavity 103, and the upper part of the power supply cavity is sealed by a power supply cavity sealing cover 102. The lower part of the power supply cavity 103 is provided with a sealed power supply outlet 106, and a power supply cable 107 is used for supplying electricity to the control device 205, the vibration detection device, the axial damping system and the circumferential damping system through the lower sealed power supply outlet 106.

The vibration monitoring system includes: a fourth outer tube 201, a vibration measuring sensor 202, a detection device gland 203, a control device gland 204, a control device 205 and a signal transmission cable 206.

The fourth outer tube 201 is hollow cylindrical, threads are arranged at the upper end and the lower end of the fourth outer tube, the upper end with the threads is connected with the third outer tube 101, and the lower end with the threads can be connected with the first outer tube 301. The vibration measuring sensor 202 is mounted on the vibration monitoring outer case 201 by a screw thread, and the vibration measuring sensor 202 is sealed by a detection device sealing gland 203. A control device 205 is mounted on the fourth outer tube 201, and a control device gland 204 seals the control device 205. The power supply cable 107 feeds electricity to the vibration measuring transducer 202 and the control device 205, respectively, through power supply sealing holes in the inner bore of the vibration monitoring housing 201. The vibration measuring sensor 202 transmits the measured data signal to the control device 205 through the signal transmission cable 206.

The control device 205 may include a vibration data collector and a vibration data analyzing and processing module, where the vibration data collector collects data of the vibration detecting device according to a sampling frequency set by a program, and then the vibration data analyzing and processing module processes and analyzes the vibration data, compares the processed data with data set in the program, and determines whether the circumferential vibration strength is greater than a set value. And if the underground vibration data is larger than the set threshold value, starting the circumferential damping system to reduce the vibration of the drilling tool. When the downhole vibration data is smaller than the set threshold value, the control device 205 controls the circumferential damping system to stop working, so that the aims of eliminating the damage of the circumferential vibration of the downhole drilling tool to the drilling tool and the drilling bit, improving the rock breaking efficiency of the drilling bit and effectively prolonging the service life of the tool are fulfilled.

In the present embodiment, the axial damping system starts or stops the damping operation by receiving a signal (second execution signal) from the control device 205. The axial damping system comprises a second outer tube 401, a damping balance 402, a pressure conducting bore 406. The second outer tube 401 is generally cylindrical, the upper portion of the second outer tube is provided with threads to be connected with the outer shell 201 in a threaded manner, and the inside of the second outer tube 401 is similar to the third outer tube 101 and is also provided with a stepped hole.

In the present embodiment, the axial damping device 4 starts or stops the damping operation by receiving a signal (second execution signal) from the control device 205. The axial damping device 4 comprises a second outer tube 401; a pressure transmission hole 406, the pressure transmission hole 406 being provided on the wall of the second outer tube 401; a damper balance portion 402 that is slidably fitted in the second outer tube 401, the damper balance portion 402 receiving an internal pressure of the drilling fluid acting on an upper end surface thereof in the second outer tube 401, the damper balance portion 402 having a protrusion located above the pressure transmission hole 406, an outer wall of the protrusion abutting against an inner wall of the second outer tube 401, and a lower end surface of the protrusion receiving an external pressure input from the pressure transmission hole 406; the reducing mechanism is arranged in the damping balance part 402 and provided with a first flow passage penetrating through the second outer pipe along the length direction of the second outer pipe, the control device 205 is electrically connected with the reducing mechanism, and the control device 205 can control the reducing mechanism to change the inner diameter of the first flow passage so as to control the size of the inner pressure.

The shock absorbing balance portion 402 is a T-shaped cylinder having an inner through hole (i.e., a first flow passage). The damping balance part 402 comprises a protruding part which is arranged on the outer wall of the damping balance part 402, and the outer wall of the protruding part is tightly attached to the inner wall of the second outer tube to form a cylinder at the upper part and to be matched with the inner circular hole of the second outer tube 401. The lower end is provided with threads to connect with a lower connector 408. As shown in fig. 1, the middle section is a spline section and is connected with the lower end of the second outer tube 401 by splines. The damping balance part can transmit torque and move up and down through being matched with a wall spline of the first flow passage.

As shown in fig. 2, the lower end of the shock-absorbing balance portion 402 extends out of the second outer tube 401 and is connected to a lower joint 408. The lower joint 408 may be connected to a tool located below the tool damping means, and the distance between the second outer tube 401 and the tool above the second outer tube and the lower joint 408 and the tool below the second outer tube may be changed relatively during the movement of the damping balance 402.

The outer cylindrical surface of the upper end of the damping balance part 402 is provided with a sealing combination 403 (such as a sealing ring or a sealing pair), and the sealing combination 403 is used for sealing between the upper cylindrical section of the damping balance part 402 and the inner wall of the second outer tube 401 of the axial damping system.

In this embodiment, one of the internal and external pressures is downward and the other is upward. For convenience of implementation, the upper end surface area of the shock-absorbing balance portion 402 is larger than the lower end surface area thereof, so that the direction of the internal pressure is downward. Further, the outer wall of the damping balance portion 402 is reduced in diameter by the reducing step in the top-down direction. Drilling fluid introduced into the pressure conducting hole 406 (between the composite damping tool and the borehole wall) acts on the variable diameter step.

A pressure conducting hole 406 is provided in the lower portion of the second outer tube 401 below the boss, and a filter 407 may be provided thereon. Typically, a filter 407 may be disposed inside the pressure transfer bore 406. In this embodiment, the pressure transfer bore 406 is used to transfer annulus drilling fluid pressure and the filter 407 filters the incoming fluid to avoid debris from plugging the axial damping system pressure transfer bore 406.

The damping balance part can be provided with a reducing mechanism; the control device 205 is connected with the reducing mechanism; the control device 205 can control the reducing mechanism to change the inner diameter of the first flow passage. The control device 205 may control the magnitude of the current, the magnitude of the voltage, or the magnitude of the magnetic field input to the reducing mechanism, so as to control the size of the reducing mechanism. In consideration of various ways of implementing diameter change by the diameter changing mechanism, whether from a structure or a form of combining the structure with software, the embodiment is not limited herein.

Specifically, the reducing mechanism may be a reducing solenoid valve 404 disposed on a wall of the first flow passage. The power supply cable 107 and the signal transmission cable 206 are connected to the electromagnetic variable diameter valve 404.

The reducing solenoid valve 404 includes a plurality of solenoid reducing valve blocks 4041 arranged along a circumference, for example, the number of the solenoid reducing valve blocks 4041 may be 2 to 10. A pressure spring 405 is arranged between two adjacent electromagnetic variable-diameter valve blocks. The control device 205 controls two adjacent electromagnetic variable diameter valve blocks 4041 to move away from or close to each other, thereby changing the size of the circumference surrounded by the plurality of electromagnetic variable diameter valve blocks 4041.

Specifically, two adjacent electromagnetic variable diameter valve blocks 4041 may attract or repel each other through a magnetic field generated by electromagnetic induction, and correspondingly, the control device 205 may control the magnitude of the current input to the electromagnetic variable diameter valve blocks 4041, thereby controlling the magnitude of the magnetic field generated by each electromagnetic variable diameter valve block 4041.

In the present embodiment, the electromagnetic variable diameter valve 404 has a structure as shown in fig. 10A and 10B, and the electromagnetic variable diameter valve 404 includes a pressure spring 405 and an electromagnetic variable diameter valve block 4041. Fig. 10A shows an initial state of the electromagnetic variable diameter valve 404 (which may also be understood as an unreduced state, in which the electromagnetic variable diameter valve 404 may not be energized, that is, the control device 205 cuts off between the power supply mechanism and the electromagnetic variable diameter valve 404), and the electromagnetic variable diameter valve block 4041 is in an open state under the action of the compression spring 405, and at this time, the electromagnetic variable diameter valve block 4041 forms an overflow hole of a circular hole, which may be the same as or equal to the diameter of the inner through hole of the damping balance portion 402.

Specifically, as shown in fig. 11A to 12B, a circumferential groove for accommodating the reducing solenoid valve 404 is formed on the wall of the first flow passage; when the diameter of the reducing solenoid valve 404 is not reduced, the inner diameter of the first flow passage is not changed along the length direction. In the present embodiment, the number of the reducing solenoid valves 404 may be plural (two or more). A plurality of reducing solenoid valves 404 are arranged along the extending direction of the outer pipe. The number of the circumferential grooves is the same as that of the reducing solenoid valves 404 and corresponds to that of the reducing solenoid valves one to one. A certain distance may be formed between two adjacent reducing solenoid valves 404, so as to achieve a better shock absorption effect.

In this embodiment, fig. 10B shows a state after the electromagnetic variable diameter valve 404 is activated, and the electromagnetic variable diameter valve block 4041 forms a circular closed passage around the closed passage, and the diameter of the closed passage is smaller than the inner diameter of the first flow passage of the damping balance portion 402. As the inner diameter of the first flow passage is reduced, the area of the upper end of the damping balance portion 402 is increased, and thus a larger downward force is generated by the drilling fluid acting on the damping balance portion 402.

In the present embodiment, fig. 11A and 11B show a diagram in which the variable electromagnetic valve 404 of the vibration damping balance portion is not actuated. As shown in fig. 11A, the upper end surface of the damper balance portion 402 receives the tool internal pressure Pp, the upper end surface area is Auo, the diameter-variable step surface receives the annulus pressure Pa, and the diameter-variable step surface area is Ado.

Fig. 11B shows the force applied to the damping balance portion 402, which is applied by the downward force Fo and the upward force Fa, and the force WOB of the drilling fluid in the axial damping system on the lower end surface of the damping balance portion 402 is also considered for precise control. Thus, the relationship between these forces is as follows:

at this time, the resultant force applied to the vibration-damping balance portion 402 is upward, and therefore, as shown in fig. 13A, the vibration-damping balance portion 402 is at the top dead center position (where the inner wall of the outer tube is provided with a diameter-variable portion for limiting).

Fig. 12A and 12B show the force diagrams after the damper balance portion electromagnetic variable diameter valve is activated. As shown in fig. 12A, the upper end surface of the vibration damping balance portion 402 receives the tool internal pressure Pp, the upper end surface area is Aso, the diameter-variable step surface receives the annulus pressure Pa, and the lower end surface area is Ado.

In comparison with fig. 11A and 12A, the area of the upper end surface of the damper balance portion 402 increases as the variable diameter solenoid valve 404 is activated. Fig. 12B shows the force applied to the damper balance portion 402, which is applied by the upper and lower forces Fs and the upward force Fa, and also considers the force WOB of the drilling fluid in the axial damping system on the lower end surface of the damper balance portion 402. The relationship between these forces is as follows:

at this time, the resultant force applied to the damper balance portion 402 is downward, and therefore, as shown in fig. 13B, the damper balance portion 402 is at the bottom dead center position. In general, the resultant force of the shock absorbing balance part 402 downward is greater than the resultant force of the shock absorbing balance part upward by 20-40 KN.

In this case, when the bit is jumped, the bit moves the damping flat piston 402 upward through the lower joint 408, and then the damping balance 402 moves downward again to the bottom dead center under the hydraulic thrust (fig. 13B). Under the hydraulic pushing, the axial vibration of the drilling tool and the drill bit is greatly reduced by the hydraulic balancing action, so that the drilling tool and the drill bit are protected, the rock breaking efficiency of the drill bit is improved, and the service life of the drilling tool is prolonged.

After the different electromagnetic variable diameter valves 404 are started, the upper end surfaces of the damping balance parts 402 are different, so that the damping strength ranges are different, and the number of the electromagnetic variable diameter valves 404 in the damping execution system is 1-10 in a normal condition.

The vibration measuring sensor 202 firstly collects vibration data of the drilling tool at a preset sampling frequency, then processes the vibration data and sends out the vibration data in a vibration signal mode. Wherein the vibration signal comprises a vibration type and a vibration intensity. The control device 205 is capable of receiving the vibration signal from the vibration measuring sensor and analyzing and comparing the vibration signal. The control device 205 first determines whether the vibration signal is axial vibration or circumferential vibration. When the vibration is an axial vibration, the control device 205 compares the vibration signal with a first threshold value. When greater than the first threshold, the control device 205 activates the axial damping system. When the vibration is a circumferential vibration, the control device 205 compares the vibration signal with a second threshold value. When greater than the second threshold, the control device 205 activates the circumferential damping system. When the vibration is axial vibration and circumferential vibration at the same time, the control device 205 compares the vibration signal with the first threshold and the second threshold at the same time. When the vibration value is larger than the first threshold value and/or the second threshold value, the control device 205 starts the axial damping system and/or the circumferential damping system, so that the axial damping of the drilling tool can be realized, the circumferential damping of the drilling tool can be realized, the damage to the drill bit caused by the vibration is avoided, the rock breaking efficiency of the drill bit is improved, and the service life of the tool can be effectively prolonged.

It is to be understood that the above description is intended to be illustrative, and not restrictive. Many embodiments and many applications other than the examples provided will be apparent to those of skill in the art upon reading the above description. The scope of the present teachings should, therefore, be determined not with reference to the above description, but should instead be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled. The disclosures of all articles and references, including patent applications and publications, are hereby incorporated by reference for all purposes. The omission in the foregoing claims of any aspect of subject matter that is disclosed herein is not intended to forego such subject matter, nor should the inventors be construed as having contemplated such subject matter as being part of the disclosed subject matter.

Claims

1. A method of damping vibration of a drilling tool, comprising the steps of:

when the vibration type is composite vibration, comparing the acquired vibration data with a preset first threshold value, starting an axial damping system when the vibration data is greater than the first threshold value, comparing the acquired vibration data with a preset second threshold value, and starting a circumferential damping system when the vibration data is greater than the second threshold value;

the circumferential damping system and the axial damping system are hydraulic devices; the circumferential damping system comprises:

a first outer tube;

2. The method of claim 1, wherein the step of obtaining vibration data of the drill by the vibration measuring sensor is performed by the vibration measuring sensor being provided on an outer peripheral wall of the drill.

3. The method of claim 1, wherein when the vibration type is axial vibration, the step of comparing the acquired vibration data with a preset first threshold value, and when the vibration data is greater than the first threshold value, the step of activating an axial damping system further comprises:

4. The method for damping vibration of a drilling tool according to claim 1, wherein when the vibration type is circumferential vibration, the step of comparing the acquired vibration data with a preset second threshold value, and when the vibration data is greater than the second threshold value, the step of activating a circumferential damping system further comprises:

5. The method for damping vibration of a drill according to any one of claims 1 to 4, wherein in the step of obtaining vibration data of the drill by the vibration measuring sensor, the vibration measuring sensor obtains the vibration data of the drill every 1 second or 2 seconds.

6. The method of damping a drilling tool of claim 1, wherein the axial damping system comprises:

a second outer tube connectable to the first outer tube;

a pressure conducting bore disposed in a wall of the second outer tube;

the reducing mechanism is arranged in the damping balance part and provided with a first flow channel penetrating through the second outer pipe in the length direction, the control device is electrically connected with the reducing mechanism and can control the reducing mechanism to change the inner diameter of the first flow channel, so that the inner pressure is controlled.

7. The method of damping of a drilling tool according to claim 6, wherein the circumferential damping system is disposed above the axial damping system.

8. The method of damping of a drilling tool according to claim 1, wherein the vibration measuring sensor is disposed above the circumferential damping system and the axial damping system.