CN111946250B

CN111946250B - Gas-liquid coupling power conversion system for gas drilling

Info

Publication number: CN111946250B
Application number: CN202010761240.9A
Authority: CN
Inventors: 李宬晓; 周长虹; 邓虎; 许期聪; 赵友; 肖洲; 杨晓峰; 董仕明; 黄述春; 王跃江
Original assignee: China National Petroleum Corp; CNPC Chuanqing Drilling Engineering Co Ltd
Current assignee: China National Petroleum Corp; CNPC Chuanqing Drilling Engineering Co Ltd
Priority date: 2020-07-31
Filing date: 2020-07-31
Publication date: 2022-03-01
Anticipated expiration: 2040-07-31
Also published as: CN111946250A

Abstract

The invention provides a gas-liquid coupling power conversion system for gas drilling. The system can provide driving force for the hydraulic actuating mechanism and comprises a gas-liquid coupling stamping device, a hydraulic oil control device and an oil tank assembly, wherein the gas-liquid coupling stamping device comprises a pneumatic impactor and a reciprocating pump, a piston of the pneumatic impactor can collide with a pump piston of the reciprocating pump to transmit mechanical energy to the pump piston, and the reciprocating pump can convert the mechanical energy into pressure energy of hydraulic oil; the hydraulic oil control device comprises a flow distribution unit, an energy storage unit and a regulating unit; the oil tank assembly can recover hydraulic oil flowing out of the hydraulic actuator and comprises an oil storage tank and a supercharger. The invention has the advantages that the pneumatic impactor and the pump piston move relatively independently without mutual influence, the defects of poor coordination of combined action and the like caused by rigid connection are overcome, the pressure and the flow of hydraulic oil can be read and controlled to obtain relatively stable output characteristics, and a stable power source is provided for a hydraulic actuating mechanism.

Description

Gas-liquid coupling power conversion system for gas drilling

Technical Field

The invention relates to the field of petroleum and natural gas drilling, in particular to a gas-liquid coupling power conversion system for gas drilling.

Background

At present, the exploration difficulty of domestic oil and gas resources is getting bigger and bigger, the target is shifted to difficult-to-exploit oil and gas reservoirs with low yield, low pressure, low permeability and the like, wherein the difficult-to-exploit oil and gas reservoirs comprise a large number of water-sensitive, salt-sensitive, alkali-sensitive and clastic rock stratums, the permeability is sharply reduced after the difficult-to-exploit oil and gas reservoirs react with drilling filtrate, and the reservoir protection or the discovery of new gas reservoirs is difficult to realize by using a conventional drilling method. Practical experience at home and abroad shows that the gas drilling technology is more favorable for discovering and protecting oil and gas reservoirs, the horizontal well can increase the control area of a single well, effectively improve the yield of the single well, prolong the stable production time, reduce the land utilization and environmental pollution, and has remarkable economic benefit. The combination of the horizontal well and the gas drilling technology can furthest liberate hydrocarbon reservoirs and open up a new path for finding and reasonably developing low-pressure low-permeability hydrocarbon reservoirs, but the combination of the horizontal well and the gas drilling technology lacks a downhole power drilling tool specially used for gas drilling.

The current downhole power drills used for gas drilling have air screws and self-rotating air hammers. The air screw is improved from a traditional mud screw drilling tool, the screw drilling tool has hard mechanical characteristics due to the fact that drilling fluid is not compressible, the screw drilling tool is widely applied to directional and horizontal drilling due to the advantage, and the mechanical characteristics originally possessed by the screw motor are changed from 'hard' to 'soft' due to the fact that gas is compressible. Although the air screw adopts a series of structural optimization and improvement aiming at the compressibility of gas, the air screw can be basically used for foam and inflation drilling, when the circulating medium is dry gas and atomization, the problems of large output torque and rotation speed influence by load, short service life, easy runaway of a motor and the like exist, and the reliability is seriously lacked. The autorotation type air hammer adopts the rotation and impact modes to break rock, gas not only generates impact power but also drives a drill bit to rotate, effective drilling can be realized only by very high pressure, the stress condition is severe during working, the whole service life of a drilling tool is short, and the output torque is limited and is difficult to meet practical requirements. Because of the lack of reliable underground power drilling tools, gas drilling can only drive a drill string to rotate by means of the force of a rotary table or a top drive at present, so that a drill bit is driven to break rock, and the drill bit cannot slide to drill a control track. This approach results in gas drilling that can only use the most primitive centralizer combination to drill straight, steady-slope and horizontal sections, with lag trajectory control and inefficiency, and the whipstock section cannot drill at all. The conventional method is to adopt gas drilling to accelerate and control leakage in a straight well section and a steady slope section, and replace slurry to be converted into conventional drilling in a slope making section, so that the development and application of a gas drilling technology are greatly limited.

Disclosure of Invention

In view of the deficiencies in the prior art, it is an object of the present invention to address one or more of the problems in the prior art as set forth above. For example, one of the objectives of the present invention is to provide a gas-liquid coupled power conversion system for gas drilling to make up for the deficiency of the actuator directly driven by gas to do work.

In order to achieve the purpose, the invention provides a gas-liquid coupling power conversion system for gas drilling.

The gas-liquid coupling power conversion system for gas drilling can provide driving force for a hydraulic actuating mechanism, and can comprise: the hydraulic oil system comprises a gas-liquid coupling stamping device, a hydraulic oil control device and an oil tank assembly, wherein the gas-liquid coupling stamping device comprises a pneumatic impactor and a reciprocating pump, wherein the pneumatic impactor can convert pressure energy of gas into mechanical energy of a piston, and the reciprocating pump is fixedly connected with the pneumatic impactor along the same axis; the reciprocating pump comprises a pump cylinder barrel, a pump piston, a pump cylinder seat and a return elastic piece; the pump cylinder barrel is fixedly connected with an outer cylinder barrel of the pneumatic impactor; the pump piston is arranged in the pump cylinder barrel, a first cavity for the collision between the piston and the pump piston to exchange mechanical energy is formed between the upper end part of the pump piston and the lower end part of the piston, the first cavity can be communicated with the outside so as to discharge the gas after pushing the impactor piston to move out of the stamping device, and the pump piston is provided with an upper end part capable of bearing the collision between the piston of the pneumatic impactor and a transition part forming a seal with the inner wall of the pump cylinder barrel and a lower end part inserted into the interior of the pump cylinder seat; the pump cylinder base is provided with a cavity for inserting the lower end part of the pump piston and an oil suction and discharge channel capable of sucking and discharging oil; the pump cylinder seat is arranged in the pump cylinder barrel, a second cavity capable of containing hydraulic oil is formed among the pump cylinder seat, the pump piston and the inner wall of the pump cylinder barrel, and the second cavity is communicated with the oil suction and discharge channel; the return elastic piece is arranged in the second cavity, one end of the return elastic piece is arranged on the pump piston, and the other end of the return elastic piece is arranged on the pump cylinder seat; the piston of the pneumatic impactor can reciprocate along the axis and can collide with a pump piston of a reciprocating pump so as to transfer mechanical energy to the pump piston, and the reciprocating pump can convert the mechanical energy of the pump piston into pressure energy of hydraulic oil in the second cavity; the hydraulic oil control device includes: the hydraulic oil recovery device comprises a flow distribution unit, an energy storage unit and an adjusting unit, wherein the flow distribution unit comprises a pump oil valve and an oil return valve which are all one-way valves, the pump oil valve can receive hydraulic oil flowing out of an oil suction and discharge channel and output the hydraulic oil, and the hydraulic oil recovered by an oil tank assembly can be conveyed to the oil suction and discharge channel after passing through the oil return valve; the energy storage unit can store the hydraulic oil output by the oil pumping valve so as to enable the pressure of the hydraulic oil to reach a rated value; under the condition that the pressure of the hydraulic oil reaches a rated value, the adjusting unit can receive the hydraulic oil, perform pressure adjustment and/or flow adjustment on the received hydraulic oil, and then convey the adjusted hydraulic oil to the hydraulic actuating mechanism; the oil tank assembly can recover hydraulic oil flowing out of the hydraulic actuating mechanism and comprises an oil storage tank and a supercharger; wherein, the oil storage tank can store the hydraulic oil of retrieving, and the booster can carry out the pressure boost to the hydraulic oil of retrieving and handle.

According to one or more exemplary embodiments of the present invention, the pump piston may have a first center bore disposed along the axis, and the pump cylinder block may have a second center bore disposed along the axis. Further, the stamping device may further include a filler pipe connected to the reservoir of the reservoir assembly along an axis through the pneumatic impactor, the first central bore and the second central bore.

According to one or more exemplary embodiments of the present invention, the pump piston has a first exhaust hole, the pump cylinder base has a second exhaust hole, and the first cavity can communicate with the outside through the first exhaust hole, the cavity, and the second exhaust hole.

According to one or more exemplary embodiments of the present invention, the stamping device may further include an end through joint fixedly connected to the oil suction/discharge passage, the end through joint is connected to the flow distribution unit downstream of the stamping device through a high-pressure pipeline, and hydraulic oil in the second cavity may be discharged to the energy storage unit or hydraulic oil in the oil tank assembly may be supplemented to the second cavity by switching on/off states of the pump oil valve and the return oil valve.

According to one or more exemplary embodiments of the present invention, the pump oil valve is provided with a first oil inlet and a first oil outlet, and the return oil valve is provided with a second oil inlet and a second oil outlet; the flow distribution unit further comprises a flow distribution valve seat used for installing an oil return valve and an oil pumping valve, and a first oil inlet channel, a first oil outlet channel, a second oil inlet channel and a second oil outlet channel are arranged on the flow distribution valve seat, wherein the first oil inlet channel can be communicated with a first oil inlet, the first oil outlet channel can be communicated with a first oil outlet, the second oil inlet channel can be communicated with a second liquid inlet, and the second oil outlet channel can be communicated with a second oil outlet.

According to one or more exemplary embodiments of the present invention, the regulating unit may include a pressure control valve and a flow control valve, wherein the pressure control valve includes a pressure control valve spool and a pressure control valve seat block, the pressure control valve spool is disposed in the pressure control valve seat block, the pressure control valve spool has a pressure control valve oil inlet and a pressure control valve sequence port, the pressure control valve oil inlet is in a normally closed state and is configured to be opened after being subjected to a force to reach the rated value so as to receive hydraulic oil discharged from the energy accumulating unit.

According to one or more exemplary embodiments of the present invention, the pump oil valve may be provided with a first oil inlet and a first oil outlet, and the return oil valve may be provided with a second oil inlet and a second oil outlet; the flow distribution unit can further comprise a flow distribution valve seat used for installing an oil return valve and an oil pumping valve, and a first oil inlet channel, a first oil outlet channel, a second oil inlet channel and a second oil outlet channel are arranged on the flow distribution valve seat, wherein the first oil inlet channel can be communicated with the first oil inlet, the first oil outlet channel can be communicated with the first oil outlet, the second oil inlet channel can be communicated with the second liquid inlet, and the second oil outlet channel can be communicated with the second oil outlet.

In one or more exemplary embodiments of the present invention, the first oil inlet may include at least one first sub oil inlet, the first oil inlet passage may include at least one first sub oil inlet passage, the first sub oil inlets and the first sub oil inlet passages are the same in number and can correspond to each other one by one, and the first sub oil inlets in the corresponding relationship are communicated with the first sub oil inlet passage; the first oil outlet can comprise at least one first sub oil outlet, the first oil outlet channel can comprise at least one first sub oil outlet channel, the number of the first sub oil outlets and the number of the first sub oil outlet channels are the same, the first sub oil outlets and the first sub oil outlet channels can correspond to each other one by one, and the first sub oil outlets in the corresponding relation are communicated with the first sub oil outlet channels.

In one or more exemplary embodiments of the present invention, the second oil inlet may include at least one second sub oil inlet, the second oil inlet passage may include at least one second sub oil inlet passage, the second sub oil inlets and the second sub oil inlet passages are the same in number and can correspond to each other one by one, and the second sub oil inlets and the second sub oil inlet passages in the corresponding relationship are communicated; the second oil outlet can comprise at least one second sub oil outlet, the second oil outlet channel can comprise at least one second sub oil outlet channel, the number of the second sub oil outlets and the number of the second sub oil outlet channels are the same, the second sub oil outlets and the second sub oil outlet channels can be in one-to-one correspondence, and the second sub oil outlets in the corresponding relationship are communicated with the second sub oil outlet channels.

In one or more exemplary embodiments of the present invention, the flow control valve may include a flow control valve spool disposed in the flow control valve seat block, the flow control valve spool being capable of regulating a flow rate of the hydraulic oil flowing in and having a flow control valve oil inlet capable of receiving the hydraulic oil discharged from the pressure control valve sequence port and a flow control valve oil outlet capable of discharging the hydraulic oil after the flow rate is regulated.

In one or more exemplary embodiments of the present invention, the flow control valve may further include a valve block gland, and the pressure control valve seat block, the flow control valve seat block and the valve block gland are coaxially and sequentially connected, wherein the pressure control valve seat block is further provided with a pressure control valve oil inlet channel connected to the pressure control valve oil inlet, one end of the pressure control valve oil inlet channel is connected to the pressure control valve oil inlet, and the other end of the pressure control valve oil inlet channel can receive hydraulic oil discharged from the accumulator; a pressure control valve connecting channel connected with a pressure control valve sequence port is arranged on the pressure control valve seat block, a flow control valve connecting channel connected with an oil inlet of a flow control valve is arranged on the flow control valve seat block, and the pressure control valve and the flow control valve connecting channel are communicated with each other; the flow control valve seat block is provided with a first oil discharge channel connected with an oil outlet of the flow control valve, the valve block gland is provided with a second oil discharge channel communicated with the outside, and the first oil discharge channel and the second oil discharge channel are communicated.

In one or more exemplary embodiments of the present invention, the pressure control valve oil inlet may include at least one sub-pressure control valve oil inlet, the pressure control valve oil inlet passage includes at least one sub-pressure control valve oil inlet passage, and the sub-pressure control valve oil inlets are in one-to-one correspondence with the sub-pressure control valve oil inlet passages.

In one or more exemplary embodiments of the present invention, the pressure control valve sequence port may include at least one sub-pressure control valve sequence port, the flow control valve oil inlet may include at least one sub-flow control valve oil inlet, the pressure control valve connection passage may include at least one sub-pressure control valve connection passage, the flow control valve connection passage includes at least one sub-flow control valve connection passage, and the sub-pressure control valve sequence port, the sub-pressure control valve connection passage, the sub-flow control valve connection passage and the sub-flow control valve connection passage correspond to the sub-flow control valve oil inlets one to one.

In one or more exemplary embodiments of the present invention, the flow control valve oil outlet may include at least one sub-flow control valve oil outlet, the first oil drain passage may include at least one sub-first oil drain passage, the second oil drain passage may include at least one sub-second oil drain passage, the sub-flow control valve oil outlet, the sub-first oil drain passages and the sub-second oil drain passages correspond to each other one by one, and the sub-second oil drain passages are open to the outside.

According to one or more exemplary embodiments of the present invention, a supercharger may include a first joint, a first outer pipe, a second joint, and a supercharger cylinder, the first and second joints being respectively provided at both ends of the first outer pipe; the pressure cylinder is arranged inside the first outer pipe and comprises a first flange, a pressure cylinder barrel, a second flange, a piston, an elastic component and a sealing component, wherein the piston, the elastic component and the sealing component are arranged in the pressure cylinder barrel; the piston is located between second flange and the elastic component to can get into hydraulic oil in the pressure boost cylinder or slide in the pressure boost cylinder under elastic component's effect, elastic component can be the state of compression under the effect of piston, and seal assembly sets up in order to realize sealed between piston and pressure boost cylinder inner wall.

According to one or more exemplary embodiments of the present invention, the oil reservoir may include: the oil cylinder comprises a third joint, a second outer pipe, a fourth joint and an oil storage cylinder barrel, wherein the third joint and the fourth joint are respectively arranged at two ends of the second outer pipe, and the third joint is connected with the second joint; the oil storage cylinder is arranged inside the second outer pipe and comprises a third flange, an oil storage cylinder barrel and a fourth flange, wherein the third flange and the fourth flange are respectively positioned at two ends of the oil storage cylinder barrel and can fix the oil storage cylinder barrel in the second outer pipe, one end of the oil storage cylinder barrel where the third flange and the fourth flange can be plugged is both arranged on the third flange, an outward end straight joint is arranged on the third flange and can be connected with an end straight joint on the second flange through a pipeline, an outward end straight joint is also arranged on the fourth flange and can be used as an inlet for recovering hydraulic oil from a hydraulic actuating mechanism and an outlet for discharging the recovered hydraulic oil from the oil return valve.

According to one or more exemplary embodiments of the present invention, the elastic assembly may include at least two springs connected to each other by a spring seat, the at least two springs being disposed along an axial direction of the pressurizing cylinder barrel.

Compared with the prior art, the beneficial effects of the invention can comprise at least one of the following contents:

(1) the piston of the pneumatic impact mechanism returns through position feedback and autonomous gas distribution, and the pump piston returns under the action of the return mechanism, and the two move independently without mutual influence. No matter how the load of the hydraulic actuating mechanism is, as long as compressed gas is input, the piston of the pneumatic impactor can continuously impact the piston of the reciprocating pump to transfer momentum, and the defects that in the prior art, the pneumatic piston and the hydraulic plunger are rigidly connected to cause poor joint action coordination and the return stroke of the pneumatic piston is tired by the load are overcome.

(2) The prior art lacks energy storage device, is difficult to eliminate flow and pressure pulsation, realizes the pressurize steady voltage of system, can't provide continuous power for hydraulic motor, and output torque and rotational speed can't satisfy the on-the-spot requirement. The pressure control valve of the invention enables the oil path for supplying liquid to the hydraulic actuating mechanism from the accumulator to have constant load, namely the opening pressure of the pressure control valve. No matter whether the hydraulic actuating mechanism acts on an external load or not, when the internal pressure of the accumulator is not reached, the reciprocating pump continuously charges the accumulator until the pressure reaches PS (namely a preset value), the pressure control valve is opened, and pressure oil is output to the hydraulic actuating mechanism. If the external load is large enough, the accumulator reaches the opening pressure of the pressure control valve after short-time liquid filling, the system works under the working pressure determined by the external load, the pressure is higher than PS, the pressure control valve is always in a fully open state, excessive pressure loss is avoided, the hydraulic execution mechanism can obtain continuous pressure and flow supply, and the hydraulic execution mechanism can overcome the external load equivalent to the maximum working pressure of the accumulator to do work under an ideal condition and can sufficiently meet the field requirement.

(3) In the prior art, an actuating mechanism is directly driven by gas to do work, and the gas is compressible, belongs to elastic drive, is poor in stability and difficult to control, and cannot be used as an underground power drilling tool. The invention transfers the compressed gas drilling energy to liquid in an impact pressurization mode, changes elasticity into rigidity by utilizing the incompressible characteristic of the liquid, and provides a stable underground power source for gas drilling.

Drawings

The above and other objects and features of the present invention will become more apparent from the following description taken in conjunction with the accompanying drawings, in which:

FIG. 1 illustrates a schematic diagram of a gas-liquid coupled power conversion system for gas drilling in an exemplary embodiment of the invention;

fig. 2 is a schematic structural view of a gas-liquid coupling punching device according to an exemplary embodiment of the present invention;

FIG. 3 shows a schematic diagram of a reciprocating pump in an exemplary embodiment of the invention;

FIG. 4 illustrates a schematic structural view of a pump cylinder block in an exemplary embodiment of the invention;

FIG. 5 shows a left, right side and cross-sectional view of the pump cylinder block of FIG. 4;

FIG. 6 is a schematic diagram showing the construction of a hydraulic oil control apparatus according to another exemplary embodiment of the present invention;

FIG. 7 is a schematic diagram showing a configuration of a flow distribution unit in another exemplary embodiment of the present invention;

FIG. 8 shows a schematic view of an energy charging seat in another exemplary embodiment of the invention;

FIG. 9 shows a schematic view of an adjustment unit in another exemplary embodiment of the invention;

fig. 10 shows another schematic view of an adjustment unit in another exemplary embodiment of the invention;

FIG. 11 shows a schematic view of a supercharger in yet another exemplary embodiment of the present invention;

FIG. 12 shows a schematic view of a reservoir in accordance with yet another exemplary embodiment of the present invention;

description of the main reference numerals:

1100-pneumatic impactor; 1200-reciprocating pump, 1210-pump cylinder, 1220-pump piston, 1230-pump cylinder seat, 1231-second center hole, 1232-second vent hole, 1233-suction/discharge oil channel, 1240-return elastic element, 1250-oil filling pipe, 1260-retaining ring, 1270-guide ring; 2100-flow distribution unit, 2110-oil pumping valve, 2111-first sub oil inlet, 2112-first sub oil outlet; 2120-oil return valve, 2121-second sub oil inlet, 2122-second sub oil outlet; 2130-a flow distribution valve seat, 2131-a first oil inlet channel, 2132-a first oil outlet channel, 2133-a second oil inlet channel, 2134-a second oil outlet channel and 2135-a plug; 2200-an energy storage unit, 2210-an energy accumulator, 2220-an energy accumulator seat, 2221-an oil inlet passage of the sub energy accumulator, 2222-an energy accumulator connecting passage and 2223-a second oil return passage; 2300-an adjusting unit, 2310-a valve core of the pressure control valve, 2311-an oil inlet of the sub-pressure control valve, 2312-a sequence port of the sub-pressure control valve and 2313-an oil outlet of the sub-pressure control valve; 2320-pressure control valve seat block, 2321-sub-pressure control valve oil inlet passage, 2322-sub-pressure control valve connecting passage; 2330-flow control valve core, 2331-flow control valve oil inlet, 2332-flow control valve oil outlet; 2340-flow control valve seat block, 2341-sub flow control valve connecting passage, 2342-sub first oil discharge passage; 2350-valve block gland, 2351-second oil drain channel; 2361-inner hexagonal screw, 2362-inner hexagonal plug, 2363-sealing gasket, 2364-O type seal ring; 2370-a first oil return passage; 2380-exhaust channel; 3000-hydraulic actuator; 4000-a fuel tank assembly; 4110-a first joint; 4120-a first outer tube; 4130-a second linker; 4140-pressure cylinder, 4141-first flange, 4142-pressure cylinder, 4143-second flange, 4144-piston, 4145-resilient assembly, 4146-first end pass-through, 4147-spring seat, 4148-first seal, 4149-guide ring; 4150-a seal assembly; 4160-a first gas conducting cavity; 4210-third linker; 4220-a second outer tube; 4230-fourth linker; 4240-oil storage cylinder, 4241-third flange, 4242-oil storage cylinder barrel, 4243-fourth flange, 4244-second-end through joint and 4245-second sealing ring; 4250-a second air conducting cavity; a-a first cavity, B-a second cavity, and C-a cavity.

Detailed Description

Hereinafter, the gas-liquid coupling power conversion system for gas drilling according to the present invention will be described in detail with reference to the accompanying drawings and exemplary embodiments.

Fig. 1 shows a schematic configuration diagram of a gas-liquid coupled power conversion system for gas drilling in an exemplary embodiment of the invention.

In an exemplary embodiment of the invention, the gas-liquid coupling power conversion system for gas drilling can provide stable hydraulic driving force for a downhole hydraulic actuator, and the system can comprise a gas-liquid coupling stamping device, a hydraulic oil control device and a tank assembly.

The gas-liquid coupled ram device may include, among other things, a pneumatic impactor 1100 and a reciprocating pump 1200 as shown in fig. 1. The pneumatic impactor 1100 can convert the pressure energy of the gas into the mechanical energy of the piston, and the pneumatic impactor 1100 and the reciprocating pump 1200 can be arranged along the same axis and can be fixedly connected. The piston of the pneumatic impactor 1100 is capable of reciprocating along an axis and colliding with the pump piston of the reciprocating pump 1200 to transmit mechanical energy to the pump piston, the reciprocating pump 1200 is capable of converting the mechanical energy of the pump piston into pressure energy of hydraulic oil, and the reciprocating pump 1200 is capable of outputting and absorbing the hydraulic oil.

The hydraulic oil control apparatus may include: a pump oil valve 2110, a return oil valve 2120, an energy storage unit 2200 and a regulating unit 2300. The oil pump valve 2110 and the oil return valve 2120 may be main components of the flow distribution unit. As shown in fig. 1, the pump oil valve 2110 may receive the hydraulic oil flowing out of the reciprocating pump 1200 and output the hydraulic oil, and the energy storage unit 2200 may store the hydraulic oil output from the pump oil valve 2110 so that the pressure of the hydraulic oil reaches a rated value; in the case where the pressure of the hydraulic oil reaches the rated value, the adjusting unit 2300 can receive the hydraulic oil in the connecting line, perform pressure adjustment and flow adjustment on the received hydraulic oil, and then deliver the adjusted hydraulic oil to the hydraulic actuator 3000; the hydraulic actuator 3000 can perform work under the action of the stabilized hydraulic oil.

The oil tank assembly 4000 can recover the hydraulic oil flowing out of the hydraulic actuating mechanism and further can perform additional treatment on the hydraulic oil; the hydraulic oil of the tank assembly 4000 can be returned to the reciprocating pump 1200 through the oil return valve 2120.

In the present embodiment, fig. 2 shows a schematic structural diagram of a gas-liquid coupling punching device (may be simply referred to as a punching device). Figure 3 shows a schematic of the construction of a reciprocating pump.

As shown in FIG. 2, the pneumatic impactor 1100 and the reciprocating pump 1200 are coaxially disposed. In which the piston of the pneumatic impactor 1100 can reciprocate along the axis of the punching device (i.e., in the up-and-down direction of fig. 2) under the push of compressed gas to convert the pressure energy of the gas into mechanical energy of the piston.

The pneumatic impactor 1100 may include an upper joint, an adjustment pad, a dome, a semi-annular sleeve, a spring seat, an inner cylinder seat, a cushion pin, a cushion spring, an inner cylinder, a core tube, a spacer, a gas distribution sleeve, and an outer cylinder liner. Compressed gas from the upper drill string enters from the upper joint and enters a space between the spring seat and the inner cylinder seat through the air inlet hole in the air guide sleeve. Then, the gas enters an annular space formed between the inner cylinder and the outer cylinder from a side hole of the inner cylinder seat, and then enters the rear air chamber through a circumferential hole on the inner cylinder and a groove on the surface of the piston to push the piston to move downwards (i.e. from top to bottom in fig. 2) to do work. When the piston descends to the position where the inner hole on the large end of the piston is separated from the core pipe, the gas in the rear gas chamber enters the first cavity through the central hole (which is overlapped with the axis) on the piston to be decompressed and is discharged out of the stamping device. The piston continues to travel downward under inertia to collide with the pump piston 1220 at high speed to complete momentum exchange. At the moment, the piston descends to the large end of the piston and enters the middle spacer bush, and the inner diameter of the middle spacer bush is larger than that of the large end of the piston, so that an annular space for gas to pass through is formed between the large end of the piston and the middle spacer bush. The gas enters the front air chamber through the groove on the surface of the piston and the annular space, and the small end of the piston seals the side hole on the gas distribution sleeve. The high-pressure gas in the front gas chamber pushes the piston to move upwards (from bottom to top in figure 2) to do work, when the piston moves upwards to the small end of the piston and passes through the side hole in the gas distribution sleeve, the side hole in the gas distribution sleeve is opened, and the gas in the front gas chamber enters the first cavity through the side hole in the gas distribution sleeve to be decompressed and is discharged out of the stamping device. The gas continues to enter the pneumatic impactor 1100, forcing the piston to reciprocate along the axis, with the piston reciprocating once per cycle, colliding with the pump piston 1220. However, the present invention is not limited thereto, and other impact mechanisms capable of converting pressure energy of gas of an upper drill string during air drilling into mechanical energy of a piston, and colliding the pump piston 1220 of the reciprocating pump of the present invention by the piston may be used as the pneumatic impactor herein. In other words, the piston of the pneumatic impactor 1100 reciprocates along the axis of the ram (i.e., moves up and down in fig. 2) under the push of the compressed gas in the upper drill string to convert the pressure energy of the gas into mechanical energy of the piston, the piston of the pneumatic impactor 1100 collides with the pump piston 1220 of the reciprocating pump 1200 to transfer the mechanical energy to the pump piston 1220, and the pump piston 1220 pressurizes the hydraulic oil in the second cavity of the reciprocating pump to increase the pressure of the hydraulic oil and generate an instantaneous flow to be discharged to the downstream mechanism of the ram.

As shown in fig. 2, the reciprocating pump 1200 mainly includes a pump cylinder 1210, and a pump piston 1220, a pump cylinder seat 1230, and a return elastic member 1240 provided inside the pump cylinder 1210. The upper end of the pump cylinder 1210 is fixedly connected to the lower end of the outer cylinder of the pneumatic impactor 1100, for example, the two may be screwed, but the present invention is not limited thereto, and other connection methods are also possible. A first chamber a may be formed between the pump piston 1220 and the piston of the pneumatic impactor 1100, in which the piston collides with the pump piston 1220 and exchanges mechanical energy. The pump cylinder seat 1230 has a cavity C into which the lower end of the pump piston 1220 is inserted and which may form a seal. Here, the first chamber a may communicate with the outside through an exhaust passage, so that the gas after pushing the piston of the pneumatic impactor 1100 to reciprocate is discharged out of the punching device, that is, the gas in the first chamber a is discharged during the movement of the piston. For example, the pump piston 1220 may have a first exhaust hole, the pump cylinder holder 1230 may have a second exhaust hole 1232 (shown in fig. 5), and the first cavity a communicates with the outside through the first exhaust hole, a lower portion of the cavity C (i.e., a cavity between the lower end surface of the pump piston 1220 and the inner wall of the pump cylinder holder 1230), and the second exhaust hole 1232. Here, the gas exiting the ram is partially or completely compressed gas from the upper drill string that has been reduced in pressure after pushing the impactor piston through the drill string. However, the present invention is not limited to this, and for example, the pump cylinder or the outer cylinder may be provided with an exhaust hole for exhausting the gas entering the first chamber out of the ram.

In this embodiment, the pump piston 1220 has an upper end capable of withstanding the piston impact of the pneumatic impactor 1100, a transition portion that forms a seal with the inner wall of the pump cylinder 1110, and a lower end that is inserted inside the pump cylinder seat 1230. Specifically, the pump piston 1220 may include a first cylindrical section, a second cylindrical section, and a third cylindrical section that are fixedly coupled or integrally formed from top to bottom. The outer diameters of the first cylindrical section and the third cylindrical section are smaller than the outer diameter of the second cylindrical section, and the outer diameter of the second cylindrical section is equal to or slightly smaller than the inner diameter of the pump cylinder 1210. The upper end surface of the first cylindrical section can bear the impact of the piston of the pneumatic impactor 1100, the radial circumference of the second cylindrical section forms a seal with the inner wall of the pump cylinder 1210, and the third cylindrical section is inserted into the cavity of the pump cylinder block 1230 and forms a seal. In addition, the lower end surface of the second cylindrical section is provided with first mounting holes for mounting the return elastic pieces 1240, and the first mounting holes are uniformly distributed along the circumference of the lower end surface of the second cylindrical section. Further, a sealing member may be provided between the pump piston 1220 and the inner wall of the pump cylinder 1110, and between the lower end of the pump piston 1220 and the inner wall of the pump cylinder holder 1230.

In this embodiment, fig. 4 shows a schematic view of a pump cylinder block. Fig. 5 shows a left and right side view and a cross-sectional view of the pump cylinder block of fig. 4, wherein (a) shows a left side view of the pump cylinder block, (b) shows a right side view of the pump cylinder block, (c) shows an M-M cross-sectional view of the pump cylinder block, and (d) shows (a) a N-N cross-sectional view of the pump cylinder block.

As shown in fig. 5 (d), the pump cylinder holder 1230 may be a hollow cylinder, and the pump cylinder holder 1230 may have a cavity C into which the lower end portion of the pump piston 1220 is inserted, and a suction/discharge oil passage 1233 capable of sucking and discharging oil. As shown in fig. 2, the pump cylinder seat 1230 is disposed in the pump cylinder 1210, and a second cavity B capable of containing hydraulic oil is formed between the pump cylinder seat 1230, the pump piston 1220 and the inner wall of the pump cylinder 1210, and the second cavity B may communicate with the suction/discharge oil passage 1233 shown in fig. 5. The pump cylinder base 1230 may be a hollow cylinder, the oil suction and discharge passage 1233 may be radially opened in the pump cylinder base 1230, and one end of the oil suction and discharge passage 1233 is communicated with the second cavity B, and the other end is connected to the flow distribution unit located downstream of the ram device. Here, since the reciprocating pump operates on the single-acting principle, the second chamber has a common oil suction and discharge passage (i.e., the oil suction and discharge passage 1233), and the oil suction and discharge process is implemented by switching the on/off states of the oil pump valve and the oil return valve. The number of the oil sucking and discharging channels 1233 can be 2-8, the number is not fixed, and the oil sucking and discharging channels can be increased or decreased according to needs. A plurality of suction/discharge oil passages 1233 may be symmetrically disposed in the pump cylinder block 1230 along the axis. In addition, the upper end surface (i.e., the left end of the structure shown in fig. 4) of the pump cylinder base 1230 is further provided with second mounting holes for mounting the return elastic member 1240, and the second mounting holes are uniformly distributed along the circumference of the upper end surface of the pump cylinder base 1230 and correspond to the first mounting holes on the second cylindrical section of the pump pistons 1220 one-to-one.

As shown in fig. 2 and 3, a return elastic member 1240 may be provided in the second chamber B, and has one end mounted on the pump piston 1220 and the other end mounted on the pump cylinder seat 1230. Specifically, one end of the return elastic member 1240 is inserted into the first mounting hole, and the other end thereof is inserted into the second mounting hole. Here, both ends of the return elastic member 1240 may or may not be fixedly installed to the pump piston 1220 and the pump cylinder block 1230. The number of the return elastic members 1240 may be 4 to 12, for example, 8, the return elastic members 1240 may include return springs, and when the 8 return springs are installed, the pre-pressing spring force pushes the pump piston 2 to return to the final point, the oil absorption vacuum degree obtained by the second cavity B is not greater than 0.5bar, and the total return force of the 8 springs is greater than 500N. Meanwhile, considering the non-uniformity of the load distribution and the frictional resistance of the viscosity, the sealing, and the contact of the kinematic pair, the total pre-pressure design value of the return elastic member 1240 at the end of the return stroke of the pump piston 1220 should exceed 1000N. However, the present invention is not limited thereto, and the number of the return springs may be increased or decreased as needed.

In an embodiment, the pump piston 1220 may have a first central bore disposed along an axis and the pump cylinder seat 1230 may have a second central bore 1231 disposed along an axis as shown in FIG. 5. The gas-liquid coupled ram apparatus 1200 may further include a filler pipe 1250, the filler pipe 1250 being axially connectable to the tank assembly 4000 downstream of the ram apparatus through the pneumatic impactor 1100, the first central bore, the cavity C and the second central bore 1231 to supply hydraulic oil to the tank assembly 4000. Here, when the hydraulic motor connected to the return oil tank leaks, the amount of the hydraulic oil returned to the return oil tank after pushing the hydraulic motor to do work is reduced, and it is necessary to supplement the hydraulic oil to the return oil tank through the filler pipe 1250. For example, the other end of the filler line 8 is connected to a tank located upstream of the gas-liquid coupling ram device, and the hydraulic oil in the tank is replenished to the tank assembly 4000.

In this embodiment, as shown in fig. 2 and 3, the ram may further include a retaining ring 1260, and the retaining ring 1260 may be disposed on the inner wall of the cylinder 1210 to limit the position of the cylinder block 1230 moving downward in the cylinder 1210.

The punching device may further include a guide ring 1270 disposed between the pump piston 1220 and the inner wall of the pump cylinder 1210, and the guide ring 1270 may prevent the pump piston 1220 from directly contacting the inner wall of the pump cylinder 1210, so as to reduce friction therebetween, thereby protecting the pump piston 1220 and the pump cylinder 1210 and prolonging the service life thereof. The material of the guide ring 1270 may be polyoxymethylene, however, the present invention is not limited thereto, and other materials having the same function may be used.

The stamping device can further comprise an end straight joint connected with the oil suction and discharge channel 1233, the end straight joint can be connected with a flow distribution unit at the downstream of the stamping device through a high-pressure pipeline, and hydraulic oil in the second cavity is discharged into the energy storage unit or is connected with an oil return tank to be supplemented to the second cavity through switching of the on-off state of the flow distribution unit.

In the exemplary embodiment, the working process of the gas-liquid coupling stamping device may be as follows:

when the pump piston is impacted by the piston of the pneumatic impactor (namely during the stroke of the pneumatic impactor) and moves downwards, the pump piston moves downwards and compresses the return elastic piece and the second cavity, hydraulic oil in the second cavity is increased by extrusion pressure to generate considerable instantaneous flow, and the hydraulic oil with increased pressure is discharged into the energy storage unit through the pump oil valve of the flow distribution unit through the oil suction and discharge channel. After the piston of the pneumatic impactor returns, the pump piston moves upwards under the thrust action of the return elastic piece to supplement oil, the second cavity expands to generate suction force, and hydraulic oil in the oil tank assembly is sucked into the oil return valve of the flow distribution unit through the oil suction and discharge channel to supplement oil. For example, the maximum stroke of the piston of the reciprocating pump may be 22mm, after the piston of the reciprocating pump finishes the return stroke, the piston of the pneumatic impactor M collides with the piston when moving to S168 mm each time, energy is transferred to hydraulic oil in the cylinder (i.e., the second cavity) of the reciprocating pump through momentum exchange, and the generated pressure and flow are output to the energy storage unit through the oil pump valve.

In another exemplary embodiment of the invention, the gas-liquid coupling power conversion system for gas drilling may comprise a gas-liquid coupling punching device, a hydraulic oil control device and an oil tank assembly.

Wherein the gas-liquid coupling punching means may be the same as in the previous exemplary embodiment. The gas-liquid coupling stamping device realizes the conversion of compressed air energy → mechanical energy → hydraulic energy, but due to the specific pulsation characteristic of the impact mechanism, if the generated hydraulic energy is directly used for a rotary assembly (a hydraulic motor mechanism), the rotating speed and the torque of a motor fluctuate violently, and measures must be taken to control the pressure and the flow rate of hydraulic oil so as to obtain relatively stable output characteristics. Accordingly, the present invention provides a hydraulic oil control apparatus.

The hydraulic oil control device may include: the energy storage unit, and the flow distribution unit, the connecting pipeline and the adjusting unit which are connected in sequence. The flow distribution unit may include a pump oil valve (also referred to as a pump oil spool) and an oil return valve (also referred to as an oil return spool), both of which are check valves, the pump oil valve may receive and output hydraulic oil flowing out from the reciprocating pump, and the oil return valve may deliver recovered hydraulic oil to the reciprocating pump. The connecting pipeline can receive and circulate the hydraulic oil output by the oil pumping valve; the energy storage unit is arranged on the connecting pipeline and stores the hydraulic oil output by the oil pumping valve under the condition that the oil pressure in the connecting pipeline is lower than a rated value; the regulating unit is capable of receiving the hydraulic oil in the connecting line and performing pressure regulation and flow regulation on the received hydraulic oil in the case where the oil pressure in the connecting line is not less than a rated value. As shown in fig. 6, the flow distribution unit 2100, a connection line (not shown) and the adjustment unit 2300 may be coaxially connected in sequence from top to bottom, wherein the connection line may further be provided with an energy storage unit 2200.

In this embodiment, the flow distribution unit 2100 may include a distribution valve outer tube, a distribution valve seat, an oil return spool, and an oil pump spool. The flow distribution unit can be cylindrical, the flow distribution valve seat can be arranged in the flow distribution valve outer pipe, the flow distribution valve seat and the flow distribution valve outer pipe are coaxial, the oil return valve core and the oil pumping valve core are arranged in the flow distribution valve seat, and the oil return valve core, the oil pumping valve core and the flow distribution valve seat can be coaxial.

Fig. 7 is a schematic view of the flow distribution unit (the outer tube of the flow distribution valve is not shown), wherein (a) is a schematic view of the flow distribution unit on the oil pumping side, (b) is a schematic view of the flow distribution unit on the oil return side, and (c) is a side sectional view of the flow distribution unit. The distributing valve seat may be formed by a series of processes from a cylindrical body, and as shown in fig. 7 (a) and (b), the pump spool 2110 and the return spool 2120 may be respectively located at both axial ends of the distributing valve seat 2130.

In the present embodiment, as shown in fig. 7 (a), the pump oil spool 2110 is provided inside the distribution valve seat 2130, and is coaxial therewith. The pump oil spool 2110 may include at least one first sub-oil inlet 2111 and at least one first sub-oil outlet 2112. The valve seat 2130 may have at least one first oil inlet sub-passage 2131 and at least one first oil outlet sub-passage 2132. The first oil inlet sub-channels 2131 and the first oil inlet sub-channels 2111 are the same in number and can correspond to each other one by one, one end of each oil inlet sub-channel 2131 can be filled with hydraulic oil, and the other end of each oil inlet sub-channel is communicated with the corresponding first oil inlet sub-channel 2111. The first oil outlet sub-channels 2132 and the first oil outlet sub-channels 2112 are the same in number and can correspond to each other one by one, one end of each first oil outlet sub-channel 2132 can discharge hydraulic oil in the oil pumping valve core 2110, and the other end of each first oil outlet sub-channel 2132 is communicated with the corresponding first oil outlet sub-channel 2112.

In the present embodiment, as shown in fig. 7 (b), the oil return valve core 2120 is disposed inside the distributing valve seat 2130, and is coaxial with the distributing valve seat 2130, and the oil return valve core 2120 may include at least one second sub oil inlet 2121 and at least one second sub oil outlet 2122. The valve seat 2130 may have at least one second oil inlet passage 2133 and at least one second oil outlet passage 2134. The second oil inlet sub-channels 2133 and the second oil inlet sub-ports 2121 are the same in number and can correspond to each other one by one, one end of each of the second oil inlet sub-channels 2133 can be filled with hydraulic oil, and the other end of each of the second oil inlet sub-ports is communicated with the corresponding second oil inlet sub-port 2121. The second oil outlet sub-ports 2122 and the second oil outlet sub-channels 2134 have the same number and can correspond to each other one by one, one end of the second oil outlet sub-channels 2134 can discharge hydraulic oil in the oil return spool 2120, and the other end of the second oil outlet sub-channels 2134 is communicated with the corresponding second oil outlet sub-ports 2122.

In this embodiment, the first oil inlet sub-passage 2131, the first oil outlet sub-passage 2132, the second oil inlet sub-passage 2133 and the second oil outlet sub-passage 2134 may also have an opening in the side wall of the valve seat 2130, but the opening is only opened for the convenience of machining the internal passages, and thus the opening is sealed by a plug 2135 (shown in fig. 7 (a), (b) and (c)).

In addition, one end of the first sub oil inlet passage 2131, which is introduced with hydraulic oil, one end of the first sub oil outlet passage 2132, one end of the second sub oil inlet passage 2133, which is introduced with hydraulic oil, and one end of the second sub oil outlet passage 2134, which is discharged with hydraulic oil, may be located on an end surface of one end of the flow distributing valve block 2130.

Further, the number of the first sub oil inlet 2111, the first sub oil outlet 2112, the second sub oil inlet 2121 and the second sub oil outlet 2122 may be 2 to 8, for example, 3, 4 or 5, and the various sub oil inlets or sub oil outlets are uniformly distributed on the outer wall of the oil pumping valve core 2110.

Similarly, the number of each type of oil inlet channel and each type of oil outlet channel may be 2 to 8, for example, 3, 4, or 5, and the oil inlet channels and the oil outlet channels may be uniformly distributed around the axis of the valve seat 2130.

In this embodiment, first sub oil inlet channel quantity can be the same with the quantity of suction oil discharge channel and one-to-one, and the hydraulic oil of every suction oil discharge channel flow can both get into the first sub oil inlet channel that corresponds. The number of the second oil outlet channels can be the same as that of the oil suction and discharge channels, and the second oil outlet channels correspond to the oil suction and discharge channels one by one, and hydraulic oil flowing out of each second oil outlet channel can flow into the corresponding oil suction and discharge channels.

In this embodiment, the one end of pump oil valve oil feed can also have the oil supply pipeline through the pipe connection, and accessible outside oil tank or notes oil pipe are to the input oil supply pipeline of the same kind of pump oil valve, then pass through at least one first sub oil feed passageway flows in, follows at least one first sub oil feed passageway flows out, then through the pipe connection to the one end of at least one second sub oil feed passageway flows out from the second sub oil feed passageway again, and first sub oil feed passageway, second sub oil feed passageway and the second sub oil feed passageway one-to-one that uses in the oil supply pipeline, and do not occupy the passageway of being connected with energy storage unit.

In this embodiment, the accumulator unit may be disposed on the connection line, and may include a plurality of accumulators. As shown in fig. 6, the energy storage unit 2200 may include an outer accumulator tube (not shown), 2 accumulators 2210 and an accumulator seat 2220. The energy storage unit may be cylindrical. When the number of the accumulators exceeds 2, the accumulators may be connected in parallel. The outer pipe of the accumulator can be formed by connecting a plurality of sections of outer pipes in a threaded manner. An outer cylinder barrel can be further arranged on the energy accumulator, an annular exhaust channel can be designed between the energy accumulator shell and the outer cylinder sleeve, and airflow can play a good cooling role.

In this embodiment, fig. 8 shows a schematic view of an accumulator seat, wherein (a) is a schematic axial section and (b) is a side section.

As shown in fig. 8 (a) and (b), the accumulator set may be composed of a plurality of cylinder-like sections, and the accumulator set is provided with at least one sub-accumulator oil inlet passage 2221, an accumulator connection passage 2222, and at least one sub-second oil return passage 2223.

Both ends of the accumulator connecting passage 2222 may be connected to one accumulator, respectively. One end (e.g., the left end in fig. 8 (a)) of the sub accumulator oil inlet channel 2221 may be connected to an oil outlet end of the at least one first sub oil outlet channel 2132, and may be connected through a rubber hose, so as to introduce hydraulic oil pumped out by the oil pumping valve, and the other end (e.g., the right end in fig. 8 (a)) is used for discharging hydraulic oil, and the end may be connected to a subsequent adjusting unit through a rubber hose. The number of sub accumulator oil feed passages 2221 and the number of first sub oil outlet passages 2132 may be the same, and there may be one-to-one correspondence (for example, each sub accumulator oil feed passage 2221 must be connected to one first sub oil outlet passage 2132), for example, 2, 3, 4, and, as shown in fig. 8 (b), the sub accumulator oil feed passages 2221 may be evenly distributed around the axis of the accumulator seat. Meanwhile, the sub-accumulator oil inlet passage 2221 may also be communicated with the accumulator connection passage 2222, so that the hydraulic oil at the pump oil valve pump can be pumped into the accumulator. In fact, each sub-accumulator oil inlet passage 2221 also has an opening in the side wall of the accumulator seat, but the opening is only opened for the convenience of machining the internal passage, and thus the opening can also be sealed by a plug.

The sub-second oil return passages 2223 and the second sub-oil inlet passages may be the same in number and correspond to each other one by one, and the passages may be used for oil return, for example, hydraulic oil recovered from the oil tank assembly may flow to the oil return valve through the passages, one end of the passage (for example, the right end in fig. 8 (a)) may be introduced with hydraulic oil, and the other end (for example, the left end in fig. 8) is communicated with the oil inlet end of the corresponding second oil inlet passage, (for example, each sub-second oil return passage 2223 must be connected to one second sub-oil inlet passage), and may be connected by a rubber tube. The number of the second oil return passages 2223 may be 2, 3, 4, 8, etc.

As shown in fig. 8 (b), the sub accumulator oil inlet passage 2221 and the sub second oil return passage 2223 may be uniformly distributed around the axis of the accumulator seat.

In addition, when the number of the energy accumulators is 1, the energy accumulator seat connected with one energy accumulator needs to be sealed at one end of the energy accumulator connecting channel connected with the other energy accumulator.

In this embodiment, fig. 9 shows a schematic view of the adjusting unit of the invention.

As shown in fig. 9, the adjusting unit may include an adjusting valve outer tube (not shown), a pressure control valve, and a flow control valve, wherein the adjusting unit may be cylindrical, and both the pressure control valve and the flow control valve may be disposed inside the adjusting valve outer tube. The pressure control valve may include a pressure control valve spool 2310 and a pressure control valve seat block 2320, and the pressure control valve spool 2310 may be installed within the pressure control valve seat block 2320 and coaxially disposed. The pressure control valve spool 2310 may include at least one sub-pressure control valve oil inlet port 2311, at least one sub-pressure control valve sequence port 2312, and at least one sub-pressure control valve oil discharge port 2313, and further, the number of the sub-pressure control valve oil inlet ports 2311, the number of the sub-pressure control valve sequence ports 2312, and the number of the sub-pressure control valve oil discharge ports 2313 may all be 2 to 8, for example, all may be 3, 4, 5, and the like, and all may be uniformly distributed on the outer wall of the pressure control valve spool 2310, for example, all 3 may be uniformly distributed at 120 °.

In this embodiment, the oil inlet of the sub-pressure control valve is in a normally closed state and can be opened after being subjected to an external force to reach an opening threshold value, so that hydraulic oil with pressure caused by the outside can be introduced, and the pressure control valve can control the external hydraulic capacity by adjusting the opening pressure of the pressure control valve. The pressure control valve may be a sequence valve.

Specifically, as shown in fig. 9, the flow control valve may include a flow control valve spool 2330, a flow control valve seat block 2340 and a valve block gland 2350, the flow control valve spool 2330 may be installed in the flow control valve seat block 2340 and coaxially disposed, and the valve block gland 2350 and the pressure control valve seat block 2320 are respectively disposed at both axial ends of the flow control valve and coaxially disposed. The flow control valve spool 2330 may be provided with at least one low flow control valve oil inlet 2331 and at least one low flow control valve oil outlet 2332, further, the number of the low flow control valve oil inlets 2331 and the low flow control valve oil outlets 2332 may be 2 to 8, for example, 3, 4, 5, etc., and may be uniformly distributed on the outer wall of the flow control valve spool 2330, for example, 3 are uniformly distributed at 120 °.

In this embodiment, the valve core of the flow control valve can regulate the flow of the hydraulic oil flowing in, the oil inlet of the flow control valve can receive the hydraulic oil flowing out of the sequence port of the pressure control valve, and the oil outlet of the flow control valve can discharge the hydraulic oil after the flow is regulated. The flow control valve may be a speed valve.

In this embodiment, the pressure control valve seat block, flow control valve seat block, and valve block gland may be connected sequentially by socket head cap screws 2361.

In the present embodiment, (a) in fig. 10 shows another schematic view of the adjusting unit, and (b) shows a cross-sectional view of a D-D section in (a).

As shown in (a) of fig. 10, the pressure control valve seat block 2320 may be further provided with at least one sub-pressure control valve oil feed passage 2321. The quantity of the oil inlet channels 2321 of the sub-pressure control valve is the same as that of the oil inlet channels of the sub-energy accumulators, the oil inlet channels are in one-to-one correspondence, and one oil inlet end of each oil inlet channel 2321 of the sub-pressure control valve can be connected with one oil outlet end of the corresponding oil inlet channel of the sub-energy accumulator through a rubber pipe, so that hydraulic oil in the energy accumulators can be introduced. An oil inlet end of the sub-pressure control valve oil inlet passage 2321 may be located on an end surface of the end of the pressure control valve seat block 2320 facing away from the flow control valve seat block 2340 and have an opening connected with the outside, and the other end of the sub-pressure control valve oil inlet passage 2321 may be connected with the sub-pressure control valve oil inlets 2311 in one-to-one correspondence. Each sub-pressure control valve oil inlet passage 2321 also has an opening in the side wall of the pressure control valve seat block 2320, but the opening is made for the convenience of machining the internal passage, and therefore the opening can also be closed with a plug 2135. Further, the sub-pressure control valve oil inlet passages 2321 may be evenly distributed in the circumferential direction on the pressure control valve seat block 2320, for example, 3 oil inlet passages are evenly distributed at 120 °. In addition, even if the oil inlet passage of the sub-pressure control valve is not formed and opened from the end face of the end, which is far away from the flow control valve seat block 2340, of the pressure control valve seat block 2320, the oil inlet passage can be opened, and external hydraulic oil can be introduced.

As shown in fig. 10 (a), the pressure control valve seat block 2320 may be further provided with at least one sub-pressure control valve connection passage 2322, the flow control valve seat block 2340 may be further provided with at least one sub-flow control valve connection passage 2341, the sub-pressure control valve connection passages 2322 are equal in number to the sub-pressure control valve sequence ports 2311 and correspond one to one, the sub-pressure control valve connection passages 2322 are equal in number to the sub-flow control valve connection passages 2341 and correspond one to one, and one end of each sub-pressure control valve connection passage 2322 may be connected to the corresponding sub-pressure control valve sequence port 2311 and the other end is connected to the corresponding sub-flow control valve connection passage 2341. The number of the sub-flow control valve connecting passages 2341 is the same as that of the sub-flow control valve oil inlets 2331, and the sub-pressure control valve sequence ports 2312 are in one-to-one correspondence with the corresponding sub-flow control valve oil inlets 2331. In fact, the sub-pressure control valve connecting passage 2322 further has an opening in the side wall of the pressure control valve seat block 2320, but the opening is opened only for machining the internal passage, and therefore the opening can also be closed with the plug 2135, and the sub-flow control valve connecting passage 2341 also has an opening in the side wall of the flow control valve seat block 2340, but the opening is opened only for machining the internal passage, and therefore the opening can also be closed with the plug 2135. Further, the number of the sub-pressure control valve connecting passages 2322 and the sub-flow control valve connecting passages 2341 may be 2 to 8, for example, 3, 4, 5, etc., and may be uniformly distributed around the axis of the regulating unit, for example, 3 may be uniformly distributed at 120 °.

As shown in fig. 10 (a), the flow control valve seat block 2340 may further include at least one sub-first oil drain passage 2342, and the valve block cover 2350 may further include at least one sub-second oil drain passage 2351.

The number of the sub-first oil discharge channels 2342, the sub-flow control valve oil outlets 2332 and the sub-second oil discharge channels 2351 is the same, and every two sub-first oil discharge channels can correspond to each other one by one, for example, each sub-first oil discharge channel can be 2-8, for example, 3 or 4. The sub first oil discharge passage 2342 may be connected at one end to the corresponding sub low flow control valve oil outlet 2332 and at the other end to the corresponding sub second oil discharge passage 2351 to form an oil discharge passage from the flow control valve to the outside. The end of the sub second oil drain passage 2351 not connected to the sub first oil drain passage 2342 may be located on an end surface of the valve block gland 2350 facing away from the end of the flow control valve seat block 2340, and have an opening for draining hydraulic oil. The sub-first oil drain passages 2342 and the sub-second oil drain passages 2351 may be uniformly distributed around the axis of the adjusting unit, for example, 3 sub-first oil drain passages may be uniformly distributed at 120 °. In addition, the sub-second oil drain passage 2351 may be formed so as not to be opened from the end surface of the end of the valve block cover 2350 away from the flow control valve seat block 2340, and the hydraulic oil may be discharged to the outside.

In addition, it is also possible even if the second oil discharge passage does not exist, as long as one end of the first oil discharge passage communicates with the flow control valve oil discharge port and the other end discharges the hydraulic oil to the outside.

Because in the process of valve core movement, hydraulic oil can inevitably enter the valve, the pressure is high and can influence the opening of the valve, the adjusting unit can be further provided with at least one sub first oil return channel 2370, and the sub oil return channels are in one-to-one correspondence with and are communicated with the oil outlet 2313 of the at least one sub pressure control valve, so that the oil in the valve can be discharged. As shown in fig. 10, the sub first oil return passage 2370 may open to the end surface of the pressure control valve seat block 2320 at the end facing away from the flow control valve seat block 2340 and have an outlet, and may open to the end surface of the valve block cover 2350 at the end facing away from the flow control valve seat block 2340 and have an outlet. Further, the number of the sub first oil return passages 2370 may be 2 to 8, such as 3, 4, 5, etc., and the sub first oil return passages 2370 may be uniformly distributed around the axis of the adjusting unit, such as 3 uniformly distributed at 120 °. The opening of the sub-first oil return passage 2370 on the side close to the flow control valve (the left end as shown in fig. 10 (a)) may be filled with hydraulic oil, and the opening on the side close to the pressure control valve may be connected to the sub-second oil return passages in a one-to-one correspondence, or may be connected by a rubber tube. In fact, each of the sub first oil return passages may have an opening on the side wall of the pressure control valve seat block, but the opening is opened only for the convenience of machining the internal passage, so the opening may also be sealed by the plug 2135.

In this embodiment, as shown in fig. 9, a mounting hole for a built-in socket head cap screw is required to be formed at each position where the socket head cap screw 2361 is arranged, and a socket head cap screw 2362 and a sealing gasket 2363 are sequentially arranged on one side of the socket head cap screw 2361 facing the opening of the mounting hole; as shown in fig. 9, since the pressure control valve spool 2310 is installed in the pressure control valve seat block 2320, an end of the pressure control valve spool 2310 facing away from the flow control valve is also provided with a hexagon socket head cap and a gasket, respectively.

In particular, the connecting lines may comprise all hydraulic oil line lines connected between the flow distribution unit, the energy storage unit and the conditioning unit.

In this embodiment, as shown in fig. 10 (b), at least one air exhaust channel 2380 may be further disposed on the outer wall of the adjusting unit, and the air exhaust channel 2380 may be a strip-shaped groove extending along the length direction of the outer wall of the adjusting unit, and further, may be 4 to 8, for example, 6. Also, the end of the vent passage 2380 that may be near the valve block gland may both be in communication with the aperture between the valve block gland and the flow control valve. Also, the air exhaust channels 2380 may be evenly distributed in the circumferential direction on the outer wall of the adjusting unit. The purpose of setting up the hole between valve block gland and the flow control valve: the lower end of the flow control valve can be connected with a motor, an exhaust passage is arranged in the center of the motor, and the hydraulic oil output by the flow control valve is connected with the motor through a hydraulic pipeline. In order not to allow gas to flush the hydraulic lines and not to withstand the gas pressure at the upper end of the motor, the exhaust passage before the valve block gland must conduct gas from within the valve block gland through the exhaust center tube bank into the motor center exhaust passage.

In this embodiment, as shown in fig. 9, at least one O-ring 2364, and further 2 to 5O-rings may be further disposed on the valve block gland 2350, and the O-rings are disposed in parallel, for example, 3O-rings, for the purpose of disposing the O-rings: the gas in the exhaust channel before the valve block is pressed and covered is sealed, and the gas is prevented from entering between the flow control valve and the motor.

The hydraulic oil line in the hydraulic oil control device of the present invention may include two, the first one being: the first sub oil inlet channel → the oil pumping valve core → the first sub oil outlet channel → the accumulator oil inlet channel (accumulator energy accumulation) → the sub pressure control valve oil inlet channel → the pressure control valve core → the sub pressure control valve connecting channel → the sub flow control valve connecting channel → the flow control valve core → the sub first oil discharge channel → the sub second oil discharge channel → the rear side can be led to the high pressure end of the hydraulic actuating mechanism.

The second one is: the low pressure end of the hydraulic actuator (and a portion of the oil may come from the pressure control valve) or the mailbox assembly → the sub first oil return passage → the sub second oil return passage → the second sub oil inlet passage → the oil return spool → the second sub oil outlet passage.

Further, the number of each passage in the hydraulic oil route may be the same and may be corresponding to each other two by two, for example, the sub first oil return passages are the same in number and correspond to the sub second oil return passages one by one, the sub second oil return passages are the same in number and correspond to the second sub oil inlet passages one by one, and the like.

In still another exemplary embodiment of the present invention, the gas-liquid coupled power conversion system for gas drilling may include: the hydraulic oil control system comprises a gas-liquid coupling stamping device, a hydraulic oil control device and an oil tank assembly.

Here, the gas-liquid coupling punch device may be the same as that in the first example embodiment, and/or the hydraulic oil control device may be the same as that in the second example embodiment.

The tank assembly may include a reservoir and a booster. As shown in fig. 11, the supercharger may include a supercharger cylinder 4140 and first, second, and

outer tubes

4120, 4130 axially connected in series.

The pressure increasing cylinder 4140 may include a piston 4144, a resilient assembly 4145, and a first flange 4141, a pressure increasing cylinder 4142, and a second flange 4143 connected in series.

The first flange 4141 and the second flange 4143 can fix the pressure cylinder 4142 in the first outer tube 4120, the second flange 4143 can also seal one end of the pressure cylinder 4142 where the second flange 4143 is located, and the first end through joint 4146 facing the second joint 4130 is further arranged on the second flange 4143, so that the hydraulic oil enters or exits the pressure cylinder 4142.

The piston 4144 and the resilient assembly 4145 may be disposed within the booster cylinder 4142, and the piston 4144 may be located between the second flange 4143 and the resilient assembly 4145 and may be capable of sliding within the booster cylinder 4142 under hydraulic oil entering the booster cylinder 4142 or under the influence of the resilient assembly 4145. A seal assembly 4150 may be disposed between the piston and the inner wall of the pressure cylinder to achieve sealing, the seal assembly 4150 may include a steckel seal and a piston seal ring, and in addition, the seal assembly may be disposed on the outer wall of the piston 4144 or the inner wall of the pressure cylinder 4142 as long as the two ends of the piston 4144 are sealed and not communicated.

In this embodiment, the first joint 4110 and the first outer tube 4120 may be connected by screw threads, and as shown in fig. 11, where the first joint 4110 and the first outer tube 4120 are connected, the first joint 4110 may be provided with external screw threads and the first outer tube 4120 may be provided with corresponding internal screw threads. The second joint 4130 and the first outer tube 4120 may be threadedly coupled, and as shown in fig. 11, the second joint 4130 may be provided with external threads and the first outer tube 4120 may be provided with internal threads at the coupling of the second joint 4130 and the first outer tube 4120. The end of the first connector 4110 facing away from the first outer tube 4120 may be internally threaded, but in this embodiment the first connector 4110 is shown plugged with a plug, and the end of the second connector 4130 facing away from the first outer tube 4120 may be externally threaded for connection to other devices.

In the present embodiment, as shown in fig. 11, the first flange 4141 and the second flange 4143 are connected to the pressure-increasing cylinder 4142, and the radial dimension of the end of the first flange 4141 and the end of the second flange 4143 connected to the pressure-increasing cylinder 4142 can be matched with the inner radial dimension of the pressure-increasing cylinder and located inside the pressure-increasing cylinder 4142, and the flange can be sealed by sleeving at least one O-ring, for example, as shown in fig. 11, two first sealing rings 4148 are sleeved between the first flange 4141 and the second flange 4143 and the pressure-increasing cylinder 4142, and the first sealing rings 4148 can be O-ring.

Moreover, the first flange 4141 and the second flange 4143 also have portions with radial dimensions adapted to the inner radial dimensions of the first outer tube 4120 and both of which can abut against the inner wall of the first outer tube 4120, while the first flange 4141 and the second flange 4143 can be fixed to the pressure increasing cylinder 4142 due to the portions of the first joint 4110 and the second joint 4130 inside the first outer tube 4120 abutting against the end of the first flange 4141 facing away from the pressure increasing cylinder 4142 and the end of the second flange 4143 facing away from the pressure increasing cylinder 4142, respectively.

In the present embodiment, the resilient assembly 4145 may include at least two springs interconnected by a spring seat 4147, the at least two springs being disposed along the axial direction of the cylinder of the booster cylinder 4142, for example: as shown in fig. 11, the number of the springs may be three, the three springs may be axially disposed in the pressurizing cylinder 4142 by two spring seats 4147, and when the springs are not compressed, one end may be connected to the first flange and the other end may be connected to the piston 4144.

In the present embodiment, as shown in fig. 11, both the first outer tube 4120 and the pressure-increasing cylinder 4142 may be hollow cylindrical, and the radial dimension of the first outer tube 4120 is larger than the radial dimension of the pressure-increasing cylinder 4142, and therefore, the first air guide chamber 4160 may be formed between the first outer tube 4120 and the pressure-increasing cylinder 4142. The first flange 4141 and the second flange 4143 may have air holes on the outer sides thereof so as to communicate the spaces inside the first joint 4110, the first air guide chamber 4160, and the second joint 4130 with each other, and since the first flange 4141 has an opening capable of connecting the space inside the first joint with the space inside the pressure cylinder 4142 on the side where the elastic member 4145 is provided, the spaces inside the pressure cylinder 4142 inside the elastic member section, the first joint, the first air guide chamber, and the second joint are communicated with each other.

In the present embodiment, a guide ring 4149 is further provided between the piston 4144 and the supercharge cylinder 4142. The guide ring 4149 prevents the piston 4144 from coming into direct contact with and rubbing against the inner wall of the pressure-increasing cylinder 4142 during the movement, and serves to protect the piston and the pressure-increasing cylinder from being damaged. The material of the guide ring may be polyoxymethylene, but the material of the guide ring of the invention is not limited thereto.

The first joint 4110, the first outer tube 4120, the second joint 4130, and the pressure cylinder 4140 may be coaxially disposed.

In this embodiment, the oil reservoir may include an oil reservoir tube 4240 and a third joint 4210, a second outer tube 4220 and a fourth joint 4230 connected in sequence, and the third joint 4210 may be connected with the second joint 4130.

The reserve tube 4240 may be located inside the second outer tube 4220 and may include a third flange 4241, a reserve tube 4242, and a fourth flange 4243, which are connected in sequence. The third and

fourth flanges

4241 and 4243 can fix the reservoir cylinder 4242 in the second outer tube 4220, both can seal off one end of the reservoir cylinder 4242, the third flange 4241 can be provided with an outward second end through joint 4244, the joint can be connected with a first end through joint 4146 on the second flange 4143 through a hose (not shown in fig. 11 and 12), and the fourth flange 4243 can be provided with a second end through joint 4244 facing the fourth joint 4230.

In this embodiment, the third joint 4210 and the second outer tube 4220 may be screwed, and the fourth joint 4230 and the second outer tube 4220 may be screwed.

In the present embodiment, as shown in fig. 12, the third flange 4241 and the fourth flange 4243 are connected to the reservoir cylinder 4242, and the radial dimension of one end of the third flange 4241 and the fourth flange 4243 connected to the reservoir cylinder 4242 may be adapted to the inner radial dimension of the reservoir cylinder and may be located inside the reservoir cylinder 4242, and the flange is sealed by fitting at least one O-ring, for example, two second sealing rings 4245 are fitted between the third flange 4241 and the fourth flange 4243 and the pressure cylinder 242 shown in fig. 12, and the second sealing ring 4245 may be an O-ring.

The third flange 4241 and the fourth flange 4243 also have a part with a radial dimension which can be matched with the inner radial dimension of the second outer pipe 4220, and the part can be abutted against the inner wall of the second outer pipe 4220, and simultaneously, the part of the third joint 4210 and the part of the fourth joint 4230 which are positioned inside the second outer pipe 4220 can be abutted against one end of the third flange 4241, which is far away from the oil storage cylinder 4242, and one end of the fourth flange 4243, which is far away from the oil storage cylinder 4242 respectively, so that the third flange 4241 and the fourth flange 4243 can fix the oil storage cylinder 4242 and further fix the oil storage cylinder.

In the present embodiment, as shown in fig. 12, both the second outer tube 4220 and the reserve cylinder 4242 may be hollow cylindrical, and the radial dimension of the second outer tube 4220 is larger than that of the reserve cylinder 4242, because a second air guide chamber 4250 may be formed between the second outer tube 4220 and the reserve cylinder 4242. The third flange 242 and the fourth flange 4243 may be provided with air holes on the outer sides thereof so as to communicate the spaces inside the third joint 4210, the second air guide chamber 4250 and the second joint 4130 with each other.

In the present embodiment, the third joint 4210, the second outer tube 4220, the fourth joint 4230, and the reserve tube 4240 may be coaxially disposed.

The working process of the oil tank assembly can be as follows: hydraulic oil from outside the tank (e.g., a hydraulic actuator or a fill tube) passes from the second end through joint 4244 at the fourth joint 4230 to the reservoir 4240, and hydraulic oil entering the reservoir 4240 can flow out of the second end through joint 4244 at the third joint 4210, through a hose to the first end through joint 4146 at the second joint 4130, then flows into the pressure increasing cylinder 14, pushes the piston 4144 to press the elastic component 4145, so that the hydraulic oil in the oil tank assembly maintains a certain pressure value, thereby avoiding negative pressure when the oil tank assembly is sucked, and in the process of oil inlet, the gas in the space at the side of the elastic component 4145 in the pressure increasing cylinder 4140 can flow out through the opening on the first flange 4141, then enters the first gas guide cavity 4160 and further can pass through the space in the second joint 4130 and the third joint 4210 and then enters the second gas guide cavity 4250; when an external device draws oil from inside the reserve tube 4240, the elastic member 4145 acts on the piston 4144 by a reaction force of compression of the spring.

In summary, the advantages of the gas-liquid coupled power conversion system for gas drilling according to the present invention may include at least one of the following:

(1) the piston of the pneumatic impact mechanism can return through the automatic air distribution through position feedback, the pump piston returns under the action of the return elastic piece, and the two move independently and do not influence each other.

(2) No matter how the load of the hydraulic actuating mechanism is, as long as compressed gas is input, the piston of the pneumatic impactor can continuously impact the piston of the reciprocating pump to transfer momentum, and the defects that the coordination of the pneumatic piston and the hydraulic plunger is poor and the return stroke of the pneumatic piston is tired by the load in the prior art are overcome.

(3) The invention transfers the compressed gas to the hydraulic oil in an impact pressurization mode, changes the elasticity into the rigidity by utilizing the incompressible characteristic of the liquid, and provides a stable underground power source for gas drilling.

(4) Because the external load of the pressure control valve can be opened only when reaching the opening pressure, the preloading of a hydraulic oil working system can be realized, when the external load is very large, the pressure control valve is always in a full-open state, the overlarge pressure loss can be avoided, and stable pressure and flow supply can be continuously output through the pressure control valve and the flow control valve.

(5) The elastic component compression in the booster makes the pressure of the hydraulic oil in the oil tank assembly keep a definite value, and in the working process in the pit, when the working tool sucks oil from the oil tank assembly, because the hydraulic oil that the oil tank assembly provided has certain pressure value, can avoid the condition of oil tank assembly negative pressure to appear.

Although the present invention has been described above in connection with exemplary embodiments, it will be apparent to those skilled in the art that various modifications and changes may be made to the exemplary embodiments of the present invention without departing from the spirit and scope of the invention as defined in the appended claims.

Claims

1. A gas-liquid coupled power conversion system for gas drilling, the system being capable of providing a driving force to a hydraulic actuator and comprising: a gas-liquid coupling stamping device, a hydraulic oil control device and an oil tank assembly, wherein,

the gas-liquid coupling stamping device comprises a pneumatic impactor and a reciprocating pump, wherein the pneumatic impactor can convert pressure energy of gas into mechanical energy of a piston, and the reciprocating pump is fixedly connected with the pneumatic impactor along the same axis; the reciprocating pump comprises a pump cylinder barrel, a pump piston, a pump cylinder seat and a return elastic piece; the pump cylinder barrel is fixedly connected with an outer cylinder barrel of the pneumatic impactor; the pump piston is arranged in the pump cylinder barrel, a first cavity for the collision between the piston and the pump piston to exchange mechanical energy is formed between the upper end part of the pump piston and the lower end part of the piston, the first cavity can be communicated with the outside so as to discharge gas after pushing the impactor piston to move out of the gas-liquid coupling stamping device, and the pump piston is provided with an upper end part capable of bearing the collision between the piston of the pneumatic impactor and a transition part forming a seal with the inner wall of the pump cylinder barrel and a lower end part inserted into the interior of the pump cylinder seat; the pump cylinder base is provided with a cavity for inserting the lower end part of the pump piston and an oil suction and discharge channel capable of sucking and discharging oil; the pump cylinder seat is arranged in the pump cylinder barrel, a second cavity capable of containing hydraulic oil is formed among the pump cylinder seat, the pump piston and the inner wall of the pump cylinder barrel, and the second cavity is communicated with the oil suction and discharge channel; the return elastic piece is arranged in the second cavity, one end of the return elastic piece is arranged on the pump piston, and the other end of the return elastic piece is arranged on the pump cylinder seat; the piston of the pneumatic impactor can reciprocate along the axis and can collide with a pump piston of a reciprocating pump so as to transfer mechanical energy to the pump piston, and the reciprocating pump can convert the mechanical energy of the pump piston into pressure energy of hydraulic oil in the second cavity;

the hydraulic oil control device includes: the hydraulic oil recovery device comprises a flow distribution unit, an energy storage unit and an adjusting unit, wherein the flow distribution unit comprises a pump oil valve and an oil return valve which are all one-way valves, the pump oil valve can receive hydraulic oil flowing out of an oil suction and discharge channel and output the hydraulic oil, and the hydraulic oil recovered by an oil tank assembly can be conveyed to the oil suction and discharge channel after passing through the oil return valve; the energy storage unit can store the hydraulic oil output by the oil pumping valve so as to enable the pressure of the hydraulic oil to reach a rated value; under the condition that the pressure of the hydraulic oil reaches a rated value, the adjusting unit can receive the hydraulic oil, perform pressure adjustment and/or flow adjustment on the received hydraulic oil, and then convey the adjusted hydraulic oil to the hydraulic actuating mechanism;

the oil tank assembly can recover hydraulic oil flowing out of the hydraulic actuating mechanism and comprises an oil storage tank and a supercharger; wherein, the oil storage tank can store the hydraulic oil of retrieving, and the booster can carry out the pressure boost to the hydraulic oil of retrieving and handle.

2. The gas-liquid coupled power conversion system for gas drilling of claim 1, wherein the pump piston has a first central bore disposed along an axis, and the pump cylinder block has a second central bore disposed along an axis.

3. The gas-liquid coupling power conversion system for gas drilling according to claim 2, wherein the gas-liquid coupling punching device further comprises an oil filling pipe, and the oil filling pipe passes through the pneumatic impactor, the first central hole and the second central hole along the axis and is connected with the oil storage tank of the oil tank assembly.

4. The gas-liquid coupling power conversion system for gas drilling according to claim 1, wherein the pump piston has a first vent hole, the pump cylinder seat has a second vent hole, and the first cavity can communicate with the outside through the first vent hole, the cavity and the second vent hole.

5. The gas-liquid coupling power conversion system for gas drilling according to claim 1, wherein the gas-liquid coupling punching device further comprises an end straight joint fixedly connected with the oil suction and discharge channel, the end straight joint is connected with a flow distribution unit at the downstream of the gas-liquid coupling punching device through a high-pressure pipeline, and hydraulic oil in the second cavity can be discharged to the energy storage unit or hydraulic oil in the oil tank assembly can be supplemented to the second cavity through switching of on-off states of the oil pump valve and the oil return valve.

6. The gas-liquid coupling power conversion system for gas drilling according to claim 1, wherein a first oil inlet and a first oil outlet are formed in the pump oil valve, and a second oil inlet and a second oil outlet are formed in the oil return valve;

the flow distribution unit further comprises a flow distribution valve seat used for installing an oil return valve and an oil pumping valve, and a first oil inlet channel, a first oil outlet channel, a second oil inlet channel and a second oil outlet channel are arranged on the flow distribution valve seat, wherein the first oil inlet channel can be communicated with a first oil inlet, the first oil outlet channel can be communicated with a first oil outlet, the second oil inlet channel can be communicated with a second liquid inlet, and the second oil outlet channel can be communicated with a second oil outlet.

7. The gas-liquid coupled power conversion system for gas drilling according to claim 1, wherein the regulating unit comprises a pressure control valve and a flow control valve, wherein,

the pressure control valve comprises a pressure control valve core and a pressure control valve seat block, the pressure control valve core is arranged in the pressure control valve seat block, the pressure control valve core is provided with a pressure control valve oil inlet and a pressure control valve sequence port, the pressure control valve oil inlet is in a normally closed state and is configured to be opened after being stressed to reach the rated value so as to receive hydraulic oil discharged by the energy storage unit.

8. The gas-liquid coupling power conversion system for gas drilling according to claim 1, wherein the pressure booster comprises a first joint, a first outer pipe, a second joint and a pressure boosting cylinder, and the first joint and the second joint are respectively arranged at two ends of the first outer pipe; the pressure cylinder is arranged inside the first outer pipe and comprises a first flange, a pressure cylinder barrel, a second flange, a piston, an elastic component and a sealing component, wherein the piston, the elastic component and the sealing component are arranged in the pressure cylinder barrel; the piston is located between second flange and the elastic component to can get into hydraulic oil in the pressure boost cylinder or slide in the pressure boost cylinder under elastic component's effect, elastic component can be the state of compression under the effect of piston, and seal assembly sets up in order to realize sealed between piston and pressure boost cylinder inner wall.

9. The gas-liquid coupled power conversion system for gas drilling as recited in claim 8, wherein the oil storage tank comprises: the oil cylinder comprises a third joint, a second outer pipe, a fourth joint and an oil storage cylinder barrel, wherein the third joint and the fourth joint are respectively arranged at two ends of the second outer pipe, and the third joint is connected with the second joint; the oil storage cylinder is arranged inside the second outer pipe and comprises a third flange, an oil storage cylinder barrel and a fourth flange, wherein the third flange and the fourth flange are respectively positioned at two ends of the oil storage cylinder barrel and can fix the oil storage cylinder barrel in the second outer pipe, one end of the oil storage cylinder barrel where the third flange and the fourth flange can be plugged is both arranged on the third flange, an outward end straight joint is arranged on the third flange and can be connected with an end straight joint on the second flange through a pipeline, an outward end straight joint is also arranged on the fourth flange and can be used as an inlet for recovering hydraulic oil from a hydraulic actuating mechanism and an outlet for discharging the recovered hydraulic oil from the oil return valve.

10. The gas-liquid coupled power conversion system for gas drilling according to claim 8, wherein the elastic assembly comprises at least two springs interconnected by a spring seat, and the at least two springs are arranged along the axial direction of the cylinder body of the booster cylinder.