阅读说明：本技术 一种气体钻井用气液耦合冲压装置 (Gas-liquid coupling stamping device for gas drilling ) 是由 李宬晓 范黎明 邓虎 韩烈祥 邓柯 庞平 赵友 廖兵 温杰 王虎 于 2020-06-09 设计创作，主要内容包括：本发明提供了一种气体钻井用气液耦合冲压装置,所述装置包括沿同一轴线固定连接的气动冲击器和往复泵,其中,所述往复泵包括泵缸筒、泵活塞、泵缸座和回程弹性件,泵缸筒与气动冲击器的外缸筒固定连接,泵活塞设置在泵缸筒内且泵活塞与活塞之间形成有供活塞与泵活塞碰撞的第一腔体,第一腔体与外界连通；泵缸座设置在泵缸筒中且泵缸座、泵活塞和泵缸筒之间形成第二腔体,第二腔体与吸排油通道连通；回程弹性件设置在第二腔体中且其两端分别作用在泵活塞和泵缸座上。本发明具有气动冲击器活塞与泵活塞独立运动、克服了两者刚性连接导致联合动作协调性差、气动冲击器活塞回程时受负载拖累的缺陷、能将压缩气体的压气能转变为液压油的压力能等优点。(The invention provides a gas-liquid coupling stamping device for gas drilling, which comprises a pneumatic impactor and a reciprocating pump, wherein the pneumatic impactor and the reciprocating pump are fixedly connected 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 collision between the piston and the pump piston is formed between the pump piston and the piston, and the first cavity is communicated with the outside; the pump cylinder seat is arranged in the pump cylinder barrel, a second cavity is formed among the pump cylinder seat, the pump piston and the pump cylinder barrel, and the second cavity is communicated with the oil suction and discharge channel; the return spring is arranged in the second cavity, and two ends of the return spring respectively act on the pump piston and the pump cylinder seat. The invention has the advantages that the pneumatic impactor piston and the pump piston move independently, the defects of poor joint action harmony caused by rigid connection of the pneumatic impactor piston and the pump piston and the defects of load tiredness caused by return stroke of the pneumatic impactor piston are overcome, the compressed air energy of compressed air can be converted into the pressure energy of hydraulic oil, and the like.)

1. A gas-liquid coupling punching device for gas drilling comprises a pneumatic impactor capable of converting pressure energy of gas into mechanical energy of a piston, and is characterized by further comprising a reciprocating pump fixedly connected with the pneumatic impactor along the same axis, wherein,

the reciprocating pump comprises a pump cylinder barrel, a pump piston, a pump cylinder seat and a return elastic piece, wherein 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 of 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, and the first cavity can be communicated with the outside so as to discharge gas after pushing the impactor piston to move out of the stamping device; the pump piston is provided with an upper end part capable of bearing the piston collision of the pneumatic impactor, 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 forming a seal, 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 the pump piston of the reciprocating pump so as to transmit 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.

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

3. The gas-liquid coupling punching device for gas drilling according to claim 1 or 2, wherein the pump piston is provided with a first vent hole, the pump cylinder seat is provided with a second vent hole, and the first cavity is communicated with the outside through the first vent hole, the cavity and the second vent hole so as to discharge the gas after pushing the impactor piston to move out of the punching device.

4. The gas-liquid coupling stamping device for gas drilling as claimed in claim 1, wherein the stamping device further comprises a retainer ring disposed on an inner wall of the pump cylinder to limit a position of the pump cylinder seat moving downward in the pump cylinder.

5. The gas-liquid coupling punching device for gas drilling according to claim 1, further comprising a guide ring disposed between the pump piston and the inner wall of the pump cylinder, wherein the guide ring is capable of avoiding direct contact between the pump piston and the inner wall of the pump cylinder to reduce friction between the pump piston and the pump cylinder.

6. The gas-liquid coupled ram apparatus for gas drilling of claim 2, further comprising an oil injection tube connected to the distribution valve assembly downstream of the ram apparatus axially through the pneumatic impactor, the first central bore, and the second central bore.

7. The gas-liquid coupling stamping device for gas drilling as claimed in claim 1, wherein the stamping device further comprises an end straight joint fixedly connected with the oil suction and discharge channel, the end straight joint is connected with a distributing valve downstream of the stamping device through a high-pressure pipeline, and hydraulic oil in the second cavity is discharged to the energy storage unit or hydraulic oil in the oil return tank is supplemented to the second cavity through switching of the on-off state of the distributing valve.

8. The gas-liquid coupling stamping device for the gas drilling as recited in claim 1, wherein the number of the oil suction and discharge channels is 2-8, and the oil suction and discharge channels are symmetrically arranged in the pump cylinder base along the axis.

9. The gas-liquid coupling stamping device for gas drilling as claimed in claim 1, wherein the number of the return elastic elements is 4-12.

10. The gas-liquid coupling stamping device for gas drilling of claim 1, further comprising a distribution valve assembly comprising a distribution valve, an energy storage unit and a return oil tank, wherein,

the distribution valve is connected with the oil suction and discharge channel, the oil suction and discharge channel can be connected with the energy storage unit through switching of the on-off state of the distribution valve, hydraulic oil in the second cavity is discharged to the energy storage unit, or the oil suction and discharge channel is connected with the oil return tank, and the hydraulic oil in the oil return tank is supplemented to the second cavity.

Technical Field

The invention relates to a gas-liquid coupling stamping device for gas drilling, which is mainly used in the field of petroleum and natural gas drilling and belongs to the technical field of gas drilling (drilling) engineering.

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. 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.

Chinese patent document CN104213829A discloses a gas drilling downhole power drilling tool, which comprises a double-acting pneumatic power short joint, a double-acting hydraulic power short joint, a closed circulation type liquid drive motor and a liquid isolation and exhaust transmission short joint. The tool converts gas energy into high-frequency reciprocating motion of a pneumatic piston through a double-acting pneumatic power nipple, and the pneumatic piston transmits the reciprocating motion to a hydraulic plunger through a connecting rod. The double-acting hydraulic power short joint realizes oil suction and oil discharge by means of reciprocating motion of a hydraulic plunger and a one-way valve, and outputs hydraulic oil with certain pressure and flow to drive a screw motor to do work. The hydraulic oil is circulated in the drilling tool in a closed manner. However, the inventors have found through research that the downhole power drilling has the following disadvantages: firstly, pneumatic piston and hydraulic pressure plunger rigid connection, pneumatic piston operating condition receive reciprocating pump plunger restriction, and power nipple joint pneumatic piston return stroke momentum of calming anger is far less than the stroke momentum, causes the return stroke smoothly or unable return stroke easily, and the power nipple joint of calming anger is difficult to continuous work. And secondly, the closed circulating type liquid drive motor adopts a screw motor type, and the hydraulic oil discharge capacity generated by the hydraulic power short joint cannot meet the requirement of the closed circulating type liquid drive motor.

Disclosure of Invention

The present invention aims to address at least one of the above-mentioned deficiencies of the prior art. For example, the invention aims to provide a gas-liquid coupling stamping device which has the advantages that a piston of a gas impactor and a piston of a hydraulic pump move relatively independently, the coordination of combined movement is good, and the return stroke of the piston of a pneumatic impactor is not limited.

In order to achieve the purpose, the invention provides a gas-liquid coupling stamping device for gas drilling, which comprises a pneumatic impactor capable of converting pressure energy of gas into mechanical energy of a piston, and a reciprocating pump fixedly connected with the pneumatic impactor along the same axis, wherein the reciprocating pump comprises a pump cylinder, a pump piston, a pump cylinder seat and a return elastic piece, the pump cylinder is fixedly connected with an outer cylinder of the pneumatic impactor, the pump piston is arranged in the pump cylinder, a first cavity for collision between the piston and the pump piston is formed between the upper end part of the pump piston and the lower end part of the piston so as to exchange the mechanical energy, and 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; the pump piston is provided with an upper end part capable of bearing the piston collision of the pneumatic impactor, 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 forming a seal, 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 the pump piston of the reciprocating pump so as to transmit 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.

In an exemplary embodiment of the invention, the pump piston may have a first central bore disposed along the axis and the pump cylinder block has a second central bore disposed along the axis.

In an exemplary embodiment of the invention, the pump piston may have a first venting hole, the pump cylinder block may have a second venting hole, and the first chamber may be in communication with the outside through the first venting hole, the cavity and the second venting hole to vent gas that has pushed the impactor piston through movement out of the punching device.

In an exemplary embodiment of the invention, the punching device may further comprise a retainer ring disposed on an inner wall of the pump cylinder to limit a position of the pump cylinder seat moving downward in the pump cylinder.

In an exemplary embodiment of the present invention, the punching device may further include a guide ring disposed between the pump piston and the inner wall of the pump cylinder, the guide ring being capable of avoiding direct contact of the pump piston with the inner wall of the pump cylinder to reduce friction between the pump piston and the pump cylinder.

In an exemplary embodiment of the invention, the ram apparatus may further include a filler tube connected to the port valve assembly downstream of the ram apparatus along an axis through the pneumatic impactor, the first central bore and the second central bore.

In an exemplary embodiment of the invention, the stamping device may further include an end through joint fixedly connected with the oil suction and discharge channel, the end through joint is connected with a distribution valve assembly downstream of the stamping device through a high-pressure pipeline, and hydraulic oil in the second cavity is discharged to the energy storage unit or hydraulic oil in the oil return tank is supplemented to the second cavity through switching of the on-off state of the distribution valve assembly.

In an exemplary embodiment of the present invention, the number of the oil suction and discharge channels may be 2 to 8, and the oil suction and discharge channels are symmetrically arranged in the cylinder block along the axis.

In an exemplary embodiment of the present invention, the number of the return springs may be 4 to 12.

In an exemplary embodiment of the invention, the stamping device further comprises a flow distribution valve assembly, the flow distribution valve assembly comprises a flow distribution valve, an energy storage unit and an oil return tank, wherein the flow distribution valve is connected with the oil suction and discharge channel, and can connect the oil suction and discharge channel with the energy storage unit through switching of the on-off state of the flow distribution valve to discharge hydraulic oil in the second cavity to the energy storage unit, or connect the oil suction and discharge channel with the oil return tank to supplement hydraulic oil in the oil return tank to the second cavity.

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

(1) the piston of the pneumatic impact mechanism and the pump piston are not directly connected and move relatively independently without mutual influence;

(2) the defects that the coordination of the combined action is poor and the return stroke of the pneumatic piston is tired by load caused by rigid connection of the pneumatic piston and the hydraulic plunger 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.

Drawings

FIG. 1 shows a schematic diagram of a gas-liquid coupled ram apparatus for gas drilling according to an exemplary embodiment of the present invention;

FIG. 2 shows a schematic view of the reciprocating pump of FIG. 1;

FIG. 3 shows a schematic structural view of the pump cylinder block of FIG. 1;

FIG. 4 shows a left side view of the pump cylinder block of FIG. 3;

FIG. 5 shows a right side view of the pump cylinder block of FIG. 3;

FIG. 6 shows a cross-sectional view A-A of the pump cylinder block of FIG. 3;

figure 7 shows a cross-sectional view of the pump cylinder block of figure 4 taken along the line C-C.

The reference numerals are explained below:

the device comprises an M-pneumatic impactor, a 1-pump cylinder barrel, a 2-pump piston, a 3-pump cylinder seat, a 4-return elastic piece, a 5-guide ring, a 6-retainer ring, a 7-end straight joint, an 8-oil injection pipe, 301-a second central hole, 302-a second exhaust hole and 303-an oil suction and discharge channel.

Detailed Description

Hereinafter, the gas-liquid coupling punching apparatus for gas drilling according to the present invention will be described in detail with reference to the exemplary embodiments and the accompanying drawings. It should be noted that "first," "second," "third," and the like are merely for convenience of description and for ease of distinction, and are not to be construed as indicating or implying relative importance. "left," "right," "upper," "lower," "inner," "outer," and the like are merely for convenience in describing and establishing relative orientations or positional relationships, and do not indicate or imply that the referenced components must have that particular orientation or position.

Fig. 1 shows a schematic structural diagram of a gas-liquid coupling punching device for gas drilling according to an exemplary embodiment of the present invention. Fig. 2 shows a schematic view of the construction of the reciprocating pump of fig. 1.

As shown in fig. 1, in the present exemplary embodiment, the gas-liquid coupling punching device for gas drilling may include a pneumatic impactor M capable of converting pressure energy of gas into mechanical energy of a piston, and further include a reciprocating pump fixedly connected to the pneumatic impactor along the same axis. Specifically, the gas-liquid coupling punching device for gas drilling mainly comprises a pneumatic impactor M (i.e. the middle box part in fig. 1) and a reciprocating pump (the lower end part in fig. 1) which are fixedly connected along the same axis. Wherein the piston of the pneumatic impactor M can reciprocate along the axis of the punching device (i.e. move up and down in fig. 1) under the push of the compressed gas to convert the pressure energy of the gas into the mechanical energy of the piston. As shown in fig. 1, the pneumatic impactor M may include an upper joint, an adjustment pad, a dome, a semi-ring sleeve, a spring seat, an inner cylinder seat, a cushion pin, a cushion spring, an inner cylinder, a core tube, a middle spacer, a gas distribution sleeve, and an outer cylinder sleeve. 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 a 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. 1) 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 move downwards under the action of inertia to collide with the pump piston 2 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 1) 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 continuously enters the pneumatic impactor M to push the piston to reciprocate along the axis, and the piston reciprocates once in each period and collides with the pump piston 2 once. 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 by which the piston collides against the pump piston 2 of the reciprocating pump of the present invention may be used as the pneumatic impactor herein. The piston of the pneumatic impactor can reciprocate along the axis and can collide with the pump piston of the reciprocating pump 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. Specifically, the piston of the pneumatic impactor M reciprocates along the axis of the punching device (i.e., moves up and down in fig. 1) 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 M collides with the pump piston 2 of the reciprocating pump to transfer the mechanical energy to the pump piston 2, and the pump piston 2 applies pressure to hydraulic oil in the second cavity of the reciprocating pump to increase the pressure of the hydraulic oil and generate instantaneous flow to be discharged to a mechanism downstream of the punching device.

In the present embodiment, the reciprocating pump includes a pump cylinder 1, a pump piston 2, a pump cylinder block 3, and a return elastic member (e.g., a return spring) 4. The pump cylinder barrel 1 is fixedly connected with an outer cylinder barrel of the pneumatic impactor M, the pump piston 2 is arranged in the pump cylinder barrel 1, a first cavity for collision between the piston and the pump piston 2 is formed between the upper end portion of the pump piston 2 and the lower end portion of the piston to exchange mechanical energy, and the first cavity can be communicated with the outside so as to discharge gas after the impactor piston is pushed to move out of the stamping device. Specifically, as shown in fig. 1 and 2, the reciprocating pump mainly includes a pump cylinder 1, and a pump piston 2, a pump cylinder block 3, and a return elastic member 4 provided inside the pump cylinder 1. Wherein, the upper end of the pump cylinder 1 is fixedly connected with the outer cylinder of the pneumatic impactor M. For example, the upper end of the pump cylinder 1 may be provided with a thread, and the pump cylinder 1 is screwed with the pneumatic hammer M. However, the invention is not limited thereto, and other connection means of the pump cylinder 1 and the pneumatic hammer M may be used. The pump piston 2 is arranged in the pump cylinder 1 along the axis and a first cavity is formed between the pump piston 2 and the piston of the pneumatic impactor M, and the piston and the pump piston 2 collide in the first cavity and exchange mechanical energy. Here, the first chamber has an exhaust passage capable of communicating with the outside, so that the gas after pushing the piston of the pneumatic impactor M to reciprocate is conveniently exhausted out of the punching device, that is, the gas in the first chamber is conveniently exhausted during the movement of the piston. For example, the pump piston 2 may have a first venting hole, and the pump cylinder block 3 may have a second venting hole 302, and the first cavity is communicated with the outside through the first venting hole, the inner cavity and the second venting hole 302, so as to discharge the gas after pushing the impactor piston to move out of the punching device. 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 the present embodiment, the pump piston 2 has an upper end portion capable of receiving a piston collision of the air hammer M, a transition portion that forms a seal with the inner wall of the pump cylinder 1, and a lower end portion that is inserted into the interior of the pump cylinder block 3. Specifically, as shown in fig. 3 to 6, the pump piston 2 may include a first cylindrical section, a second cylindrical section, and a third cylindrical section that are fixedly connected from top to bottom or integrally formed. 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 the inner diameter of the pump cylinder barrel 1. The upper end face of the first cylindrical section can bear the collision of a piston of the pneumatic impactor M, a seal is formed between the radial circumference of the second cylindrical section and the inner wall of the pump cylinder barrel 1, and the third cylindrical section is inserted into a cavity of the pump cylinder seat 3 and forms a seal. In addition, the lower end face of the second cylindrical section is also provided with first mounting holes for mounting the return elastic pieces 4, and the first mounting holes are uniformly distributed along the circumference of the lower end face of the second cylindrical section. In addition, sealing elements can be arranged between the pump piston 2 and the inner wall of the pump cylinder barrel 1 and between the lower end part of the pump piston 2 and the cavity of the pump cylinder seat 3.

FIG. 3 shows a schematic structural view of the pump cylinder block of FIG. 1; FIG. 4 shows a left side view of the pump cylinder block of FIG. 3; FIG. 5 shows a right side view of the pump cylinder block of FIG. 3; FIG. 6 shows a cross-sectional view A-A of the pump cylinder block of FIG. 3; figure 7 shows a cross-sectional view of the pump cylinder block of figure 4 taken along the line C-C.

In the present embodiment, the pump cylinder block 3 has a cavity (i.e., the left end in fig. 3) into which the lower end portion of the pump piston 2 is inserted and sealed, and a suction/discharge oil passage 303 capable of sucking and discharging oil. The pump cylinder seat 3 is arranged in the pump cylinder barrel 1, a second cavity capable of containing hydraulic oil is formed among the pump cylinder seat 3, the pump piston 2 and the inner wall of the pump cylinder barrel 1, and the second cavity is communicated with the oil suction and discharge channel 303. Specifically, as shown in fig. 3 to 7, the cylinder block 3 is a hollow cylinder, and the left end of the cylinder has a cavity matching the third cylindrical section of the pump piston 2, and the third cylindrical section of the pump piston 2 can slide in the cavity, and a sealing member is further provided on the inner wall of the cavity to form a seal. A second cavity is formed between the lower end face of the second cylindrical section of the pump piston 2, the outer wall of the third cylindrical section of the pump, the left end face of the pump cylinder barrel 1 and the inner wall of the pump cylinder barrel 1 and is used for containing hydraulic oil. An oil suction and discharge channel 303 is further provided on the pump cylinder base 3, the oil suction and discharge channel 303 is radially provided in the pump cylinder base 3, one end of the oil suction and discharge channel 303 is communicated with the second cavity, and the other end is connected with a distributing valve assembly located downstream of the punching device. Here, since the reciprocating pump operates on the single-action principle, the second chamber has a common oil suction passage and an oil discharge passage (i.e., the oil suction and discharge passage 303), the distribution valve assemblies downstream of the ram are respectively connected in the oil suction and oil discharge processes, and the oil suction and oil discharge processes are realized by switching the on-off states of the distribution valves in the distribution valve assemblies. For example, the number of the suction/discharge oil passages 303 may be 2 to 8, and the suction/discharge oil passages 303 may be symmetrically disposed in the pump cylinder block 3 along the axis. Here, the number of the suction/discharge oil passages 303 is not fixed, and may be increased or decreased as necessary. In addition, still be provided with the second mounting hole of installation return stroke elastic component 4 on the 3 left end faces of pump cylinder seat, the second mounting hole is evenly distributed and is corresponding with the first mounting hole one-to-one on the second cylinder section of pump piston 2 along 3 left end faces of pump cylinder seat circumference.

A return spring 4 is provided in the second chamber and one end of the return spring 4 is mounted on the pump piston 2 and the other end of the return spring 4 is mounted on the pump cylinder block 3. Specifically, as shown in fig. 1, the return elastic member 4 is axially installed in the second cavity, and one end of the return elastic member 4 is inserted into a first installation hole on the second cylindrical section of the pump piston 2, and the other end is inserted into a second installation hole on the left end surface of the pump cylinder block 3. Here, both ends of the return elastic member may be fixedly attached to the pump piston 2 and the pump cylinder block 3, or may not be fixedly attached. The number of the return elastic members 4 may be 4 to 12. For example, the number of the return springs 4 may be 8 return springs. Here, the 8 return springs are installed so that when the pre-pressure spring force of the return elastic member 4 pushes the pump piston 2 to return to the final point, the second chamber obtains an oil suction vacuum degree of not more than 0.5bar, and the total return force of the 8 springs is more than 500N. Meanwhile, considering the non-uniformity of load distribution and the frictional resistance of viscosity, sealing and kinematic pair contact, the total pre-pressure design value of the return elastic element 4 when the pump piston 2 of the reciprocating pump returns to the end point 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.

As shown in fig. 1, when the pump piston 2 is hit by the piston of the pneumatic impactor M (i.e., at the time of the pneumatic impactor stroke) and moves downward, the pump piston 2 moves downward and compresses the return elastic member 4 and the second cavity, hydraulic oil in the second cavity is subjected to a squeezing pressure rise to generate a considerable instantaneous flow rate, and the hydraulic oil with the pressure rise is discharged into the energy storage unit through the distributing valve via the suction/discharge oil passage 303; after the piston of the pneumatic impactor M returns (i.e. moves upward in fig. 1), the pump piston 2 moves upward under the thrust of the return elastic member 4 to perform oil replenishment, and the second cavity expands to generate suction force to suck hydraulic oil in the return oil tank through the oil suction and discharge channel 303 via the distributing valve to perform oil replenishment. For example, the maximum stroke of the piston 2 of the reciprocating pump may be 22mm, after the piston 2 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 distributing valve. In addition, the stamping device can further comprise an end straight-through joint 7 fixedly connected with the oil suction and discharge channel 303, the end straight-through joint 7 is connected with a distributing valve at the downstream of the stamping device through a high-pressure pipeline, and hydraulic oil in the second cavity is discharged into an energy storage unit or is connected with an oil return tank to be supplemented into the second cavity through switching of the on-off state of the distributing valve.

In an embodiment, the pump piston 2 may have a first central bore arranged along the axis, and the pump cylinder block 3 may have a second central bore 301 arranged along the axis. The gas-liquid coupled ram may further include a filler pipe 8, the filler pipe 8 passing through the pneumatic impactor M, the first central bore and the second central bore 301 along an axis to connect with a port valve assembly downstream of the ram. Specifically, the gas-liquid coupling punching device may further include an oil filling pipe 8, a first central hole through which the oil filling pipe 8 passes is provided on the pump piston 2 along an axis of the punching device, a second central hole 301 through which the oil filling pipe 8 passes is provided on a right end portion of the pump cylinder block 3 along the axis of the punching device, and the oil filling pipe 8 of the punching device passes through the pneumatic impactor M, the first central hole, the cavity of the pump cylinder block 3, and the second central hole 301 along the axis and then is connected to an oil return tank downstream of the punching device, so as to supply hydraulic oil to the oil return tank. 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 work decreases, and at this time, the hydraulic oil needs to be replenished to the return oil tank through the filler pipe 8. For example, the other end of the filler line 8 is connected to a booster tank located upstream of the gas-liquid coupling ram device, and the hydraulic oil in the booster tank is replenished to the return tank.

In this embodiment, the punching device may further comprise a retainer ring 6, and the retainer ring 6 may be disposed on the inner wall of the pump cylinder 1 to limit the position of the pump cylinder block 3 moving downward in the pump cylinder 1. Specifically, as shown in fig. 1, a retainer ring 6 may be further installed on the inner wall of the cylinder barrel 1, the retainer ring 6 being in contact with the lower end of the cylinder block 3, and when the pump piston 2 moves downward to apply a pushing force to the cylinder block 3, the retainer ring 6 may provide an upward reaction force to the cylinder block 3 to prevent the cylinder block 3 from moving downward under the pushing force of the pump piston 2.

In this embodiment, the stamping device may further include a guide ring 5 disposed between the pump piston 2 and the inner wall of the pump cylinder 1, and the guide ring 5 may avoid direct contact between the pump piston 2 and the inner wall of the pump cylinder 1, so as to reduce friction between the pump piston 2 and the pump cylinder 1. Here, through set up guide ring 5 between pump piston 2 outer wall and pump cylinder 1 inner wall, can avoid the direct contact between pump piston 2 and the pump cylinder 1 inner wall to reduce the friction that produces pump cylinder 1 inner wall in the motion process of pump piston 2, play protection pump piston 2 and pump cylinder 1, prolong practical life's purpose. For example, the material of the guide ring 5 may be polyoxymethylene. However, the present invention is not limited thereto, and other materials having the same function may be used

In yet another exemplary embodiment of the present invention, the gas-liquid coupling punching apparatus for gas drilling further includes a distributing valve assembly based on the above exemplary embodiments, where the distributing valve assembly includes a distributing valve, an energy storage unit, and an oil return tank, where the distributing valve is connected to the oil suction and discharge channel, and the oil suction and discharge channel is connected to the energy storage unit by switching on/off states of the distributing valve, so as to discharge hydraulic oil in the second cavity to the energy storage unit, or the oil suction and discharge channel is connected to the oil return tank, so as to supplement hydraulic oil in the oil return tank to the second cavity. The distributing valve may include a tee joint, a first check valve and a second check valve, wherein one end of the tee joint is connected to the oil suction and discharge passage through a high-pressure pipeline, the other two ends of the tee joint are respectively connected to the energy storage unit through the first check valve, the second check valve is connected to the oil return tank, the connection direction of the first check valve is from the tee joint to the energy storage unit, and the connection direction of the second check valve is from the oil return tank to the tee joint. When the second cavity discharges hydraulic oil, the hydraulic oil sequentially passes through the oil suction and discharge channel, the high-pressure pipeline, the tee joint and the first one-way valve and then enters the energy storage unit. When the second cavity absorbs oil, the hydraulic oil in the oil return tank sequentially passes through the second one-way valve, the tee joint, the high-pressure pipeline and the oil suction and discharge channel and then enters the second cavity. However, the present invention is not limited thereto, and the port valve assembly may have other structures as long as it can communicate with the suction/discharge oil passage and receive the hydraulic oil discharged from the second chamber and supplement the hydraulic oil to the second chamber.

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

in summary, the beneficial effects of the invention can include at least one of the following:

(1) the piston of the pneumatic impact mechanism can return through the automatic gas distribution by 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 affected 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.

Although the present invention has been described above in connection with the exemplary embodiments and the accompanying drawings, it will be apparent to those of ordinary skill in the art that various modifications may be made to the above-described embodiments without departing from the spirit and scope of the claims.