High frequency hydraulic drilling machine and impact control method thereof

Abstract

The present application relates to the technical field of hydraulic drilling machine, especially to a high-frequency hydraulic drilling machine and an impact control method thereof, the high-frequency hydraulic drilling machine comprising a drilling machine body, a drill tail, an impact piston, a main hydraulic circuit and a pilot control oil circuit, the drilling machine body comprising an upper cylinder body, an intermediate cylinder body, a lower cylinder body, a pilot control valve core and a rear end cover; the drill tail is installed in the drilling machine body; the impact piston is slidably arranged in the drilling machine body along an impact axis; the main hydraulic circuit is arranged in the cylinder body of the drilling machine body; the pilot control valve core is slidably arranged in the intermediate cylinder body and used for switching the communication relationship between the main hydraulic circuit and the front cavity and the rear cavity of the impact piston, so as to realize the direction control of the impact piston. The movement of the pilot control valve core is controlled by the pilot control oil circuit, so that the pilot control valve core no longer depends on the mechanical feedback of the impact piston, the inherent delay of the traditional series structure is eliminated, and the impact frequency is improved.

Description

Technical Field

[0001] This invention relates to the field of hydraulic drilling technology, and in particular to a high-frequency hydraulic drilling machine and its impact control method. Background Technology

[0002] Hydraulic drilling rigs are widely used in mining, tunneling, and other engineering projects. Their performance directly affects their adaptability to complex geological conditions, drilling efficiency, and equipment lifespan. Traditional hydraulic drilling rigs are often characterized by high impact energy and low impact frequency, making them poorly adaptable to mining conditions and resulting in low impact energy transfer efficiency. Especially under conditions of dry drilling or poor support, this can easily lead to damage to the drill rod, drill bit, and internal impact mechanism.

[0003] Chinese patent application CN115070959A discloses a rotary impact hydraulic piercing device with a stop piston and a braking chamber. Its core drawback lies in the deep coupling between the reversing logic of the control distributor and the mechanical movement of the impact piston. The movement of the distributor valve core depends on the pressure feedback or mechanical push of the impact piston at the end of its stroke. This series-connected working mode has inherent logical delays and inertia, which severely limits the increase of the impact frequency, and it is usually difficult to stably exceed 60Hz.

[0004] Therefore, it is necessary to develop a high-frequency hydraulic drilling rig that uses a completely independent pilot control oil circuit. Summary of the Invention

[0005] The purpose of this invention is to provide a high-frequency hydraulic drilling rig and its impact control method, the specific technical solution of which is as follows: A high-frequency hydraulic drilling rig, comprising: The drilling rig body includes an upper cylinder, an intermediate cylinder, a lower cylinder, a pilot control valve core, and a rear end cover; A drill shank, which is installed in the drill body, is used to receive impacts and transmit them to the drill bit; An impact piston is slidably disposed in the drill body along the impact axis for impacting the drill bit. The upper cylinder, middle cylinder, lower cylinder, pilot control valve core and rear end cover form a closed cavity for the impact piston to move. The main hydraulic circuit is located inside the cylinder of the drilling rig body and is used to drive the impact piston to reciprocate. The pilot control valve core is slidably disposed in the intermediate cylinder body and is used to switch the connection between the main hydraulic circuit and the front and rear chambers of the impact piston, thereby realizing the movement direction control of the impact piston. A pilot control oil circuit is connected to the pilot signal chamber of the pilot control valve core, and is used to independently control the commutation frequency and timing of the pilot control valve core.

[0006] Optionally, the impact piston is provided with a first piston boss and a second piston boss, which cooperate with the chamber in the main hydraulic circuit to realize the reciprocating motion of the impact piston.

[0007] Optionally, the pilot control valve core is provided with a valve core boss signal port, and the impact piston is also provided with a piston third boss; the position and size of the valve core boss signal port and the piston third boss are matched and set, and when the impact stroke and return stroke of the impact piston end, a closed cavity is formed between the valve core boss signal port and the piston third boss, and the closed cavity drives the pilot control valve core to switch direction through high pressure oil.

[0008] Optionally, the main hydraulic circuit includes a first low-pressure oil chamber, a signal chamber, a first high-pressure oil chamber, a rear pressure relief chamber, a high-pressure chamber, a pilot high-pressure oil chamber, a pilot low-pressure oil chamber, a return oil chamber, a piston second signal chamber, a second low-pressure oil chamber, a piston first signal chamber, a second high-pressure oil chamber, a third low-pressure oil chamber, a constant high-pressure chamber, and a fourth low-pressure oil chamber, wherein: The first low-pressure oil chamber, the second low-pressure oil chamber, and the third low-pressure oil chamber are all connected to an external low-pressure oil source; Both the first high-pressure oil chamber and the second high-pressure oil chamber are connected to an external high-pressure oil source.

[0009] Optionally, the main hydraulic circuit further includes a first anti-aircraft chamber and a second anti-aircraft chamber; The first anti-aircraft chamber and the second anti-aircraft chamber are composed of a first piston boss, a second piston boss, and an intermediate cylinder. The first anti-aircraft chamber and the second anti-aircraft chamber are used to cooperate with the first piston boss and the second piston boss to control the connection of other chambers in the main hydraulic circuit.

[0010] Optionally, the high-frequency hydraulic drilling rig further includes a first support ring and a second support ring, which are respectively disposed at the front end and rear end of the impact piston, and are located in front of the first protrusion of the piston and behind the second protrusion of the piston.

[0011] Optionally, the rear end cover is provided with an oil-gas chamber, and the impact piston is provided with an oil-gas channel arranged along the impact axis, and the oil-gas chamber is connected to the oil-gas channel.

[0012] Optionally, the pilot control valve core is installed in a chamber defined by the intermediate cylinder, the lower cylinder, and the impact piston.

[0013] Optionally, the high-frequency hydraulic drilling rig further includes: A high-pressure accumulator connected to an external high-pressure oil source is provided, and the high-pressure accumulator is located between the high-pressure oil source and the high-pressure oil chamber of the main hydraulic circuit. A low-pressure accumulator connected to an external low-pressure oil source, wherein the low-pressure accumulator is disposed between the low-pressure oil source and the low-pressure oil chamber of the main hydraulic circuit; The high-voltage accumulator and the low-voltage accumulator are used to absorb pressure pulsations and replenish instantaneous peak flow.

[0014] In addition, the present invention also provides an impact control method for a high-frequency hydraulic drilling rig as described above, comprising a cyclically executed retraction phase and an impact phase, wherein: Rollback phase: When the first piston boss of the impact piston is in the middle position of the constant high pressure chamber, and the left end face of the impact piston is on the right side of the left end face of the signal chamber, the pilot signal chamber of the pilot control valve core receives a high pressure signal, drives the pilot control valve core to move to the right, blocks the connection between the pilot high pressure oil chamber and the second low pressure oil chamber, and connects the low pressure oil chamber with the pilot low pressure oil chamber; at this time, the left end face of the impact piston is subjected to high pressure, driving the impact piston to retract to the right; When the impact piston retracts until the right end face of its first piston boss coincides with the right end face of the constant high pressure chamber, the constant high pressure chamber is disconnected from the signal chamber. At this time, the signal chamber, pilot control oil circuit and piston second signal chamber are in a blind chamber state. The impact piston continues to move to the right under the action of the high pressure oil at its left end until the right end face of the third piston boss of the impact piston coincides with the valve core signal chamber. The impact piston continues to move to the right, causing the oil pressure in the valve core signal chamber to rise. When the oil pressure reaches the preset value, the piston's second signal chamber, the signal chamber and the pilot signal chamber are connected, driving the pilot control valve core to start moving to the left, realizing the connection between the pilot high-pressure oil chamber and the valve core signal chamber, and disconnecting the connection between the low-pressure oil chamber and the pilot low-pressure oil chamber. At this time, the impact piston brakes and enters the impact preparation state. Impact phase: The impact piston accelerates forward under the action of high-pressure oil on the right end face of its third piston boss. During the movement, the left end face of the impact piston passes over the left end of the signal cavity. Subsequently, the right end face of the first piston boss of the impact piston passes over the right end face of the constant high pressure chamber, so that the signal cavity, the constant high pressure chamber, the piston second signal cavity and the pilot signal cavity are connected. After receiving the high-pressure signal, the pilot control valve core moves to the right, gradually closing the connection between the pilot high-pressure oil chamber, the valve core signal chamber, and the low-pressure oil chamber, and gradually realizing the connection between the low-pressure oil chambers, thus completing the rapid decoupling and switching of the low-pressure oil on the right end face of the impact piston. After the switching is completed, the impact piston decelerates and reverses direction to the right to return to its original position under the action of its left end face. Before the reversal, the impact piston has completed the impact work on the drill bit. The impact frequency of the impact piston is determined by the reversing frequency of the pilot control oil circuit.

[0015] The application of the technical solution of the present invention has at least the following beneficial effects: This invention provides a high-frequency hydraulic drilling rig and its impact control method. By completely separating the pilot control oil circuit from the main hydraulic oil circuit, the control function and power execution are decoupled. This invention controls the movement of the pilot control valve core through the pilot control oil circuit, so that the pilot control valve core no longer depends on the mechanical feedback of the impact piston, eliminating the inherent delay of the traditional series structure and improving control accuracy. The independent pilot control oil circuit of this invention allows for precise adjustment of the commutation frequency and timing of the pilot valve core via electrical signals, achieving precise digital control of the impact frequency.

[0016] In addition to the objectives, features, and advantages described above, the present invention has other objectives, features, and advantages. The invention will now be described in further detail with reference to the figures. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the structure of a high-frequency hydraulic drilling rig in a preferred embodiment of the present invention; Figure 2 This is a detailed perspective view of the high-frequency hydraulic drilling rig in a preferred embodiment of the present invention.

[0019] Among them, 1-drill rig body, 2-bristle shank, 3-impact piston, 4-first low-pressure oil chamber, 5-upper cylinder body, 6-piston first boss, 7-signal chamber, 8-pilot control oil circuit, 9-intermediate cylinder body, 10-first high-pressure oil chamber, 11-high-pressure accumulator, 12-low-pressure accumulator, 13-high-pressure oil source, 14-low-pressure oil source, 15-lower cylinder body, 16-first support ring, 17-oil and gas passage, 18-rear end cover, 19-oil and gas chamber, 20-rear end pressure relief chamber, 21-high-pressure chamber, 22-pilot high-pressure oil chamber, 23-pilot control valve core, 24-front low-pressure... 25 - Pilot signal chamber; 26 - Return oil chamber; 27 - Piston third boss; 28 - Piston second signal chamber; 29 - Second low-pressure oil chamber; 30 - Piston second boss; 31 - Piston first signal chamber; 32 - Second high-pressure oil chamber; 33 - First anti-aircraft chamber; 34 - Second support ring; 35 - Third low-pressure oil chamber; 36 - Front end oil drain channel; 37 - Second anti-aircraft chamber; 38 - Constant high-pressure chamber; 39 - Piston rear end chamber; 40 - Valve core boss signal port; 41 - Valve core signal chamber; 42 - Fourth low-pressure oil chamber; 43 - Piston third cylindrical rear end face. Detailed Implementation

[0020] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0021] Example 1: like Figure 1 As shown, this embodiment provides a high-frequency hydraulic drilling rig, including: The drilling rig body 1 includes an upper cylinder 5, an intermediate cylinder 9, a lower cylinder 15, a pilot control valve core 23, and a rear end cover 18; The drill shank 2 is installed in the drill body 1 and is used to receive impacts and transmit them to the drill bit. Impact piston 3, which is slidably disposed in the drill body 1 along the impact axis A, is used to impact the drill bit 2. The upper cylinder 5, the middle cylinder 9, the lower cylinder 15, the pilot control valve core 23 and the rear end cover 18 form a closed cavity for the impact piston 3 to move. The main hydraulic circuit is located in the cylinder of the drilling rig body 1 and is used to drive the impact piston 3 to reciprocate. The pilot control valve core 23 is slidably disposed in the intermediate cylinder 9 and is used to switch the connection between the main hydraulic circuit and the front and rear chambers of the impact piston 3 to realize the movement direction control of the impact piston 3. Pilot control oil circuit 8 is connected to pilot signal chamber 25 of pilot control valve core 23 and is used to independently control the commutation frequency and timing of pilot control valve core 23.

[0022] It should be noted that the pilot control valve core 23 is installed in a chamber jointly defined by the intermediate cylinder 9, the lower cylinder 15, and the impact piston 3. In this embodiment, the impact frequency is determined by the reversing frequency of the independent pilot control oil circuit 8, thus eliminating the constraints of the mechanical feedback loop.

[0023] In this embodiment, the impact piston 3 is provided with a first piston boss 6 and a second piston boss 30. The first piston boss 6 and the second piston boss 30 cooperate with the chamber in the main hydraulic circuit to realize the reciprocating motion of the impact piston 3.

[0024] Furthermore, the pilot control valve core 23 is provided with a valve core boss signal port 40, and the impact piston 3 is also provided with a piston third boss 27; the position and size of the valve core boss signal port 40 and the piston third boss 27 are matched and set. When the impact stroke and return stroke of the impact piston 3 are completed, a closed cavity is formed between the valve core boss signal port 40 and the piston third boss 27. The closed cavity drives the pilot control valve core 23 to switch direction through high pressure oil.

[0025] Furthermore, the impact piston 3 is also provided with a piston third cylindrical rear end face 43, which is located behind the piston third boss 27.

[0026] like Figure 2 As shown, the main hydraulic circuit includes a first low-pressure oil chamber 4, a signal chamber 7, a first high-pressure oil chamber 10, a rear pressure relief chamber 20, a high-pressure chamber 21, a pilot high-pressure oil chamber 22, a pilot low-pressure oil chamber 24, a return oil chamber 26, a piston second signal chamber 28, a second low-pressure oil chamber 29, a piston first signal chamber 31, a second high-pressure oil chamber 32, a third low-pressure oil chamber 35, a constant high-pressure chamber 38, and a fourth low-pressure oil chamber 42, wherein: The first low-pressure oil chamber 4, the second low-pressure oil chamber 29 and the third low-pressure oil chamber 35 are all connected to an external low-pressure oil source 14; The first high-pressure oil chamber 10 and the second high-pressure oil chamber 32 are both connected to an external high-pressure oil source 13.

[0027] Furthermore, the first low-pressure oil chamber 4, the third low-pressure oil chamber 35, the second low-pressure oil chamber 29, and the fourth low-pressure oil chamber 42 are distributed sequentially and at intervals along the axial direction of the impact piston. All four chambers are constantly connected to the return oil chamber 26 via independent return oil channels within the cylinder body, maintaining a low-pressure return oil state at all times. The return oil chamber 26 is the main return oil chamber of the main hydraulic circuit and is constantly connected to the external low-pressure oil port 11 (LP). The return oil from all low-pressure chambers and the return oil from the pilot circuit converge into the return oil chamber 26 and then flow back to the system oil tank, maintaining a low pressure within the chamber at all times. The rear-end pressure relief chamber 20 is located at the rear end of the cylinder body corresponding to the end of the piston's return stroke. It is connected to the control oil groove of the pilot control valve core 23 via an independent pressure relief oil channel. The pilot control valve core 23 controls the connection and disconnection between the rear-end pressure relief chamber 20 and the return oil chamber 26. When the piston returns to the end, the pilot control valve core 23 switches the oil circuit to connect the rear-end pressure relief chamber 20 and the return oil chamber 26, achieving return stroke buffering and pressure relief, reducing piston return stroke impact.

[0028] Furthermore, the signal chamber 7 is located between the front shoulders of the impact piston. As the impact piston moves axially, the signal chamber 7 alternately connects with the high-pressure distribution oil passage and the low-pressure return oil passage, providing piston position feedback signals to the pilot control circuit. When the piston reaches the end reversing position during its stroke, the signal chamber 7 connects with the high-pressure oil passage and outputs a high-pressure reversing signal; when the piston returns to the reset position, the signal chamber 7 connects with the low-pressure return oil passage and outputs a low-pressure reset signal. The piston first signal chamber 31 and piston second signal chamber 28 are located at the cylinder position corresponding to the middle shoulder of the impact piston. Both are connected to the output oil groove of the pilot control valve core 23 through independent pilot control oil passages, serving as output signal chambers for the pilot circuit. The pressure states of the piston first signal chamber 31 and piston second signal chamber 28 are switched and controlled by the pilot control valve core 23. The pressure changes are used to drive the main distribution mechanism to reverse, thereby switching the connection relationship between the high and low pressure chambers in the main hydraulic circuit, realizing the switching of the reciprocating motion state of the impact piston 3.

[0029] Furthermore, the constant high-pressure chamber 38 is the main high-pressure input chamber of the main hydraulic circuit. The constant high-pressure chamber 38 is constantly connected to the external high-pressure oil port 12 (HP) to maintain the system's high-pressure state at all times. The high-pressure oil in the chamber is divided into two output paths: one path goes through the main high-pressure oil passage to the high-pressure chamber 21 to supply oil to the main working circuit; the other path goes through an independent pilot inlet oil passage to the pilot control oil circuit to supply oil to the pilot circuit. The main high-pressure oil passage and the pilot control oil circuit are independent of each other. The high-pressure chamber 21 is the high-pressure oil distribution chamber of the main hydraulic circuit and is constantly connected to the constant high-pressure chamber 38 through the main high-pressure oil passage inside the cylinder. An axial flow distribution window is opened in the chamber wall. With the axial displacement of the impact piston 3, the flow distribution window is alternately blocked and opened by the piston shoulder, realizing the alternating connection between the high-pressure chamber 21 and the first high-pressure oil chamber 10 and the second high-pressure oil chamber 32, providing high-pressure driving force for the piston's reciprocating motion. The first high-pressure oil chamber 10 is located on the front end face of the front drive shoulder of the impact piston. When the piston returns to the set position, the piston shoulder retracts the distribution window, and the first high-pressure oil chamber 10 and high-pressure chamber 21 become connected, allowing high-pressure oil to flow in and drive the piston to perform the stroke action. During the piston stroke, the shoulder covers the distribution window again, and the first high-pressure oil chamber 10 and high-pressure chamber 21 become disconnected. The second high-pressure oil chamber 32 is located on the rear end face of the rear drive shoulder of the impact piston. When the piston reaches the set position, the piston shoulder retracts the corresponding distribution window, and the second high-pressure oil chamber 32 and high-pressure chamber 21 become connected, allowing high-pressure oil to flow in and drive the piston to perform the return stroke action. During the piston return stroke, the shoulder covers the distribution window again, and the second high-pressure oil chamber 32 and high-pressure chamber 21 become disconnected.

[0030] It should be noted that the pilot control oil circuit in this embodiment is independent of the main hydraulic circuit. The pilot control oil circuit uses the pilot control valve core 23 as the core control element and uses low-flow high-pressure oil to complete the reversing control. The oil supply, oil return, and signal feedback paths are all physically separated from the main circuit and are not affected by pressure fluctuations in the main circuit, thus significantly improving the reversing accuracy and reliability.

[0031] In this embodiment, the pilot control valve core 23 is a spool valve type two-position reversing element, which is slidably assembled in the pilot valve hole machined on the side of the cylinder block; the inner wall of the valve hole is provided with multiple sets of independent annular oil grooves along the axial direction, and each oil groove is connected to different pilot oil passages; the outer wall of the valve core is provided with multiple sets of sealing shoulders, and the relative positions of the shoulders and oil grooves are switched by axial movement to realize the switching of the on and off relationship of each oil groove and complete the reversing function.

[0032] Furthermore, the pilot control valve core 23 has a pilot high-pressure oil chamber 22 and a pilot low-pressure oil chamber 24 at its two axial ends, respectively. The pilot high-pressure oil chamber 22 and the pilot low-pressure oil chamber 24 are both independent drive chambers, which are used to cooperate to realize the switching and resetting of the pilot control valve core 23.

[0033] In this embodiment, the pilot high-pressure oil chamber 22 is the valve core reset end, which is directly connected to the constant high-pressure chamber 38 through an independent pilot inlet oil passage inside the cylinder, continuously supplying a constant pressure of pilot high-pressure oil to provide a constant reset thrust for the valve core. The pilot inlet oil passage is a small-diameter dedicated oil passage that does not flow through the high-flow-rate high-pressure oil passage in the main circuit, completely isolating the main circuit pressure spikes from interfering with the valve core reset.

[0034] In this embodiment, the pilot low-pressure oil chamber 24 is the valve core reversing end, located at the other end of the pilot control valve core 23 corresponding to the pilot high-pressure oil chamber 22. It is connected to the signal chamber 7 through an independent signal feedback oil passage inside the cylinder, and its pressure is dynamically determined by the position of the impact piston. When the piston stroke reaches the set reversing position, the signal chamber 7 is connected to high pressure, and the high-pressure oil enters the pilot low-pressure oil chamber 24 through the signal oil passage, pushing the valve core to move axially against the thrust of the pilot high-pressure oil chamber 22, thus completing the reversal. When the piston returns to the set reset position, the signal chamber 7 is connected to low-pressure return oil, the pilot low-pressure oil chamber 24 is depressurized, and the pilot high-pressure oil chamber 22 pushes the valve core to move in the opposite direction to reset.

[0035] In this embodiment, the pilot control valve core 23 achieves axial displacement through reversing and resetting, thereby controlling the opening and closing of the annular oil groove and realizing the connection between the pressure state of the first signal chamber 31 of the piston, the second signal chamber 28 of the piston, and the rear pressure relief chamber 20 and the oil circuit.

[0036] Specifically, the piston first signal chamber 31 and piston second signal chamber 28 are respectively connected to two sets of output oil grooves of the pilot valve orifice through independent pilot control oil passages. When the pilot control valve core 23 is in the reset state, the piston first signal chamber 31 is connected to the pilot high-pressure oil passage and maintains high pressure, while the piston second signal chamber 28 is connected to the pilot return oil passage and maintains low pressure. When the valve core is reversed, the oil circuit is switched, the piston second signal chamber 28 is connected to high pressure, and the piston first signal chamber 31 is connected to low pressure. The pressure change of the two sets of signal chambers serves as the pilot output signal, driving the main distribution mechanism to operate and synchronously switching the connection relationship between the high-pressure chamber 21 and the first high-pressure oil chamber 10 and the second high-pressure oil chamber 32. The pressure relief oil passage of the rear pressure relief chamber 20 is connected to the corresponding control oil groove of the pilot valve hole and is linked with the valve core reversing action. At the end of the piston return stroke and when the pilot valve core reverses, the rear pressure relief chamber 20 is connected to the return oil chamber 26 through the valve core oil groove, and the high pressure oil in the chamber is discharged into the low pressure system to achieve return stroke buffering. During the piston stroke and when the valve core is reset, the rear pressure relief chamber 20 is isolated from the return oil chamber 26.

[0037] It should be noted that the pilot control oil circuit in this embodiment has an independent oil supply, signal feedback, control output and return oil path. High pressure oil is introduced from the normal high pressure chamber 38 into the pilot high pressure oil chamber 22 through a dedicated pilot oil passage. The position signal is transmitted between the signal chamber 7 and the pilot low pressure oil chamber 24 through a dedicated signal oil passage. The control output is applied to the piston signal chamber and the pressure relief chamber through a dedicated control oil passage. Finally, the return oil flows into the return oil chamber 26 through a dedicated pilot return oil passage.

[0038] Furthermore, the main hydraulic circuit also includes a first anti-aircraft chamber 33 and a second anti-aircraft chamber 37; The first anti-aircraft chamber 33 and the second anti-aircraft chamber 37 consist of a piston first boss 6, a piston second boss 30 and an intermediate cylinder 9. The first anti-aircraft chamber 33 and the second anti-aircraft chamber 37 are used to cooperate with the piston first boss 6 and the piston second boss 30 to control the connection of other chambers in the main hydraulic circuit.

[0039] In this embodiment, the high-frequency hydraulic drilling rig further includes a first support ring 16 and a second support ring 34. The first support ring 16 and the second support ring 34 are respectively disposed at the front end and rear end of the impact piston 3, and are respectively located in front of the first protrusion 6 of the piston and behind the second protrusion 30 of the piston.

[0040] In this embodiment, the first support ring 16 and the second support ring 34 are dual-pivot radial support elements of the impact piston, respectively embedded in the front and rear annular grooves of the cylinder body bore. The inner ring surface is in clearance fit with the outer cylindrical surface of the impact piston, jointly constraining the radial degree of freedom of the piston.

[0041] It should be noted that the first support ring 16 and the second support ring 34 are distributed axially back and forth, forming a double-support guide structure. This structure withstands the radial eccentric force and lateral load generated during the high-frequency reciprocating motion of the impact piston, ensuring that the piston always performs high-precision linear reciprocating motion along the cylinder axis. This prevents radial swaying of the piston due to high-frequency reversing impact, and prevents metal-to-metal hard contact, scratching, and scoring between the piston outer circle and the cylinder inner bore, significantly extending the service life of the piston and cylinder, and adapting to the high-frequency reciprocating conditions of high-frequency hydraulic drilling rigs. In this embodiment, the support ring material has a lower hardness than the metal matrix of the piston and cylinder, and possesses self-lubricating and friction-reducing properties. During long-term high-frequency sliding of the piston, wear preferentially occurs on the support ring, preventing direct wear between the cylinder inner bore and the piston outer circle mating matrix. The first support ring 16 and the second support ring 34 are replaceable wear parts, reducing later maintenance costs; simultaneously, their low coefficient of friction reduces the frictional resistance of the piston movement, lowering the wasted energy loss of the hydraulic system.

[0042] • The auxiliary seal and cavity separation support ring is set at the axial boundary of adjacent cavities, and together with the piston shoulder, it forms a throttling gap to help separate oil cavities of different pressure levels, reduce internal leakage between cavities, and maintain the pressure stability of each cavity.

[0043] In this embodiment, the rear end cover 18 is provided with an oil-gas chamber 19, and the impact piston 3 is provided with an oil-gas channel 17 arranged along the impact axis A. The oil-gas chamber 19 is connected to the oil-gas channel 17. The oil-gas chamber 19 and the oil-gas channel 17 together constitute a piston-built-in oil-gas lubrication and cooling system, which provides continuous lubrication, heat dissipation and protection for the impact piston and internal friction pairs of the high-frequency hydraulic drilling rig.

[0044] In this embodiment, the high-frequency hydraulic drilling rig further includes: A high-pressure accumulator 11 is connected to an external high-pressure oil source 13, and the high-pressure accumulator 11 is disposed between the high-pressure oil source 13 and the high-pressure oil chamber of the main hydraulic circuit. A low-pressure accumulator 12 is connected to an external low-pressure oil source 14, and the low-pressure accumulator 12 is disposed between the low-pressure oil source 14 and the low-pressure oil chamber of the main hydraulic circuit. The high-voltage accumulator 11 and the low-voltage accumulator 12 are used to absorb pressure pulsations and replenish instantaneous peak flow.

[0045] It should be noted that, through the coordinated operation of the high-pressure accumulator 11 and the low-pressure accumulator 12, this embodiment effectively absorbs the pressure pulsation of the hydraulic system, optimizes the energy utilization efficiency, and reduces the ineffective loss of hydraulic energy through the precise timing management of the pilot control.

[0046] In addition, this embodiment also includes the impact control method of the above-mentioned high-frequency hydraulic drilling rig, including a cyclically executed retraction phase and an impact phase, wherein: Rollback phase: When the first piston boss 6 of the impact piston 3 is in the middle position of the constant high pressure chamber 38, and the left end face of the impact piston 3 is on the right side of the left end face of the signal chamber 7, the pilot signal chamber 25 of the pilot control valve core 23 receives a high pressure signal, drives the pilot control valve core 23 to move to the right, blocks the connection between the pilot high pressure oil chamber 22 and the second low pressure oil chamber 39, and connects the low pressure oil chamber 39 with the pilot low pressure oil chamber 24; at this time, the left end face of the impact piston 3 is subjected to high pressure, driving the impact piston 3 to retract to the right; When the impact piston 3 retracts until the right end face of its first piston boss 6 coincides with the right end face of the constant high pressure chamber 38, the constant high pressure chamber 38 is disconnected from the signal chamber 7. At this time, the signal chamber 7, the pilot control oil circuit 8, and the piston second signal chamber 28 are in a blind chamber state. The impact piston 3 continues to move to the right under the action of the high pressure oil at its left end until the right end face of the third piston boss 27 of the impact piston 3 coincides with the valve core signal chamber 41. The impact piston 3 continues to move to the right, causing the oil pressure in the valve core signal chamber 41 to rise. When the oil pressure reaches the preset value, the piston's second signal chamber 28, signal chamber 7 and pilot signal chamber 25 are connected, driving the pilot control valve core 23 to start moving to the left, realizing the connection between the pilot high-pressure oil chamber 22 and the valve core signal chamber 41, and disconnecting the connection between the low-pressure oil chamber 39 and the pilot low-pressure oil chamber 24. At this time, the impact piston 3 is braked and enters the impact preparation state. Impact phase: The impact piston 3 accelerates forward under the action of high-pressure oil on the right end face of its third piston protrusion 27. During the movement, the left end face of the impact piston 3 passes over the left end of the signal cavity 7. Subsequently, the right end face of the first piston protrusion 6 of the impact piston 3 passes over the right end face of the constant high pressure chamber 38, so that the signal cavity 7, the constant high pressure chamber 38, the piston second signal cavity 28 and the pilot signal cavity 25 are connected. After receiving the high-pressure signal, the pilot control valve core 23 moves to the right, gradually closing the connection between the pilot high-pressure oil chamber 22, the valve core signal chamber 41, and the low-pressure oil chamber 39, and gradually realizing the connection between the low-pressure oil chamber 42 and the low-pressure oil chamber 39, thus completing the rapid decoupling and switching of the low-pressure oil on the right end face of the impact piston 3. After the switching is completed, the impact piston 3 decelerates and reverses direction to the right to return to its original position under the action of its left end face. Before the reversal, the impact piston 3 has completed the impact work on the drill bit 2. The impact frequency of the impact piston 3 is determined by the reversing frequency of the pilot control oil circuit 8.

[0047] In this embodiment, the switching of the pilot control valve core 23 is driven by the independent pilot control oil circuit 8; Furthermore, before the impact piston 3 completes one impact phase or retraction phase, the pilot control valve core 23 completes the reversing preparation.

[0048] This embodiment provides a high-frequency hydraulic drilling rig and its impact control method. By completely separating the pilot control oil circuit from the main hydraulic oil circuit, the control function and power execution are decoupled. The high-frequency hydraulic drilling rig controls the movement of the pilot control valve core through the pilot control oil circuit, so that the pilot control valve core no longer depends on the mechanical feedback of the impact piston, eliminating the inherent delay of the traditional series structure, improving the impact frequency and control accuracy, and realizing digital precise control of the impact frequency.

[0049] The above description is only a preferred embodiment of the present invention and does not limit the scope of the present invention. All equivalent structural transformations made under the inventive concept of the present invention using the contents of the present invention specification and drawings, or direct / indirect applications in other related technical fields, are included within the protection scope of the present invention.

Claims

1. A high-frequency hydraulic drilling rig, characterized in that, include: The drilling rig body (1) includes an upper cylinder body (5), an intermediate cylinder body (9), a lower cylinder body (15), a pilot control valve core (23), and a rear end cover (18); The drill shank (2) is installed in the drill body (1) and is used to receive impact and transmit it to the drill bit; Impact piston (3), the impact piston (3) is slidably disposed in the drill body (1) along the impact axis (A) for impacting the drill bit (2), the upper cylinder (5), the middle cylinder (9), the lower cylinder (15), the pilot control valve core (23) and the rear end cover (18) form a closed cavity for the impact piston (3) to move. The main hydraulic circuit is located in the cylinder of the drilling rig body (1) and is used to drive the impact piston (3) to reciprocate. The pilot control valve core (23) is slidably installed in the intermediate cylinder (9) to switch the connection between the main hydraulic circuit and the front and rear chambers of the impact piston (3) to realize the movement direction control of the impact piston (3); Pilot control oil circuit (8), which is connected to the pilot signal chamber (25) of pilot control valve core (23), is used to independently control the commutation frequency and timing of the pilot control valve core (23).

2. The high-frequency hydraulic drilling rig according to claim 1, characterized in that, The impact piston (3) is provided with a first piston boss (6) and a second piston boss (30). The first piston boss (6) and the second piston boss (30) cooperate with the chamber in the main hydraulic circuit to realize the reciprocating motion of the impact piston (3).

3. The high-frequency hydraulic drilling rig according to claim 2, characterized in that, The pilot control valve core (23) is provided with a valve core boss signal port (40), and the impact piston (3) is also provided with a piston third boss (27). The valve core boss signal port (40) and the piston third boss (27) are matched in position and size. When the impact stroke and return stroke of the impact piston (3) are completed, a closed cavity is formed between the valve core boss signal port (40) and the piston third boss (27). The closed cavity drives the pilot control valve core (23) to switch directions through high pressure oil.

4. The high-frequency hydraulic drilling rig according to claim 3, characterized in that, The main hydraulic circuit includes a first low-pressure oil chamber (4), a signal chamber (7), a first high-pressure oil chamber (10), a rear pressure relief chamber (20), a high-pressure chamber (21), a pilot high-pressure oil chamber (22), a pilot low-pressure oil chamber (24), a return oil chamber (26), a piston second signal chamber (28), a second low-pressure oil chamber (29), a piston first signal chamber (31), a second high-pressure oil chamber (32), a third low-pressure oil chamber (35), a constant high-pressure chamber (38), and a fourth low-pressure oil chamber (42), wherein: The first low-pressure oil chamber (4), the second low-pressure oil chamber (29) and the third low-pressure oil chamber (35) are all connected to an external low-pressure oil source (14); The first high-pressure oil chamber (10) and the second high-pressure oil chamber (32) are both connected to an external high-pressure oil source (13).

5. The high-frequency hydraulic drilling rig according to claim 4, characterized in that, The main hydraulic circuit also includes a first anti-aircraft chamber (33) and a second anti-aircraft chamber (37); The first anti-aircraft chamber (33) and the second anti-aircraft chamber (37) are composed of a first piston boss (6), a second piston boss (30) and an intermediate cylinder (9). The first anti-aircraft chamber (33) and the second anti-aircraft chamber (37) are used to cooperate with the first piston boss (6) and the second piston boss (30) to control the connection of other chambers in the main hydraulic circuit.

6. The high-frequency hydraulic drilling rig according to claim 5, characterized in that, It also includes a first support ring (16) and a second support ring (34), which are respectively disposed at the front end and the rear end of the impact piston (3), and are respectively located in front of the first protrusion (6) of the piston and behind the second protrusion (30) of the piston.

7. The high-frequency hydraulic drilling rig according to claim 1, characterized in that, The rear end cover (18) is provided with an oil and gas chamber (19), and the impact piston (3) is provided with an oil and gas channel (17) arranged along the impact axis (A). The oil and gas chamber (19) is connected to the oil and gas channel (17).

8. The high-frequency hydraulic drilling rig according to claim 1, characterized in that, The pilot control valve core (23) is installed in a chamber defined by the intermediate cylinder (9), the lower cylinder (15) and the impact piston (3).

9. The high-frequency hydraulic drilling rig according to claim 1, characterized in that, Also includes: A high-pressure accumulator (11) is connected to an external high-pressure oil source (13), and the high-pressure accumulator (11) is located between the high-pressure oil source (13) and the high-pressure oil chamber of the main hydraulic circuit. A low-pressure accumulator (12) is connected to an external low-pressure oil source (14), and the low-pressure accumulator (12) is disposed between the low-pressure oil source (14) and the low-pressure oil chamber of the main hydraulic circuit; The high-pressure accumulator (11) and the low-pressure accumulator (12) are used to absorb pressure pulsations and replenish instantaneous peak flow.

10. An impact control method for a high-frequency hydraulic drilling rig as described in any one of claims 1-9, characterized in that, This includes a rollback phase and an impact phase in the cyclical execution, where: Rollback phase: When the piston first boss (6) of the impact piston (3) is in the middle position of the constant high pressure chamber (38), and the left end face of the impact piston (3) is on the right side of the left end face of the signal chamber (7), the pilot signal chamber (25) of the pilot control valve core (23) receives the high pressure signal, drives the pilot control valve core (23) to move to the right, blocks the connection between the pilot high pressure oil chamber (22) and the second low pressure oil chamber (39), and connects the low pressure oil chamber (39) with the pilot low pressure oil chamber (24); at this time, the left end face of the impact piston (3) is subjected to high pressure, driving the impact piston (3) to retract to the right; When the impact piston (3) retracts to the point where the right end face of its first piston boss (6) coincides with the right end face of the constant high pressure chamber (38), the constant high pressure chamber (38) is disconnected from the signal chamber (7). At this time, the signal chamber (7), the pilot control oil circuit (8), and the piston second signal chamber (28) are in a blind chamber state. The impact piston (3) continues to move to the right under the action of the high pressure oil at its left end until the right end face of the third piston boss (27) of the impact piston (3) coincides with the valve core signal chamber (41). The impact piston (3) continues to move to the right, causing the oil pressure in the valve core signal chamber (41) to rise. When the oil pressure reaches the preset value, the piston second signal chamber (28), signal chamber (7) and pilot signal chamber (25) are connected, driving the pilot control valve core (23) to start moving to the left, realizing the connection between the pilot high pressure oil chamber (22) and the valve core signal chamber (41), and disconnecting the connection between the low pressure oil chamber (39) and the pilot low pressure oil chamber (24). At this time, the impact piston (3) enters the impact preparation state after braking. Impact phase: The impact piston (3) is accelerated forward by the high pressure oil on the right end face of its third piston boss (27). During the movement, the left end face of the impact piston (3) passes over the left end of the signal cavity (7). Then the right end face of the first piston boss (6) of the impact piston (3) passes over the right end face of the constant high pressure chamber (38), so that the signal cavity (7), the constant high pressure chamber (38), the second piston signal cavity (28) and the pilot signal cavity (25) are connected. After receiving the high-pressure signal, the pilot control valve core (23) moves to the right, gradually closing the connection between the pilot high-pressure oil chamber (22), the valve core signal chamber (41), and the low-pressure oil chamber (39), and gradually realizing the connection between the low-pressure oil chamber (42) and the low-pressure oil chamber (39), thus completing the rapid decoupling and switching of the low-pressure oil on the right end face of the impact piston (3). After the switching is completed, the impact piston (3) decelerates and reverses direction to the right to make a return motion under the action of its left end face, and before the reversal, the impact piston (3) has completed the impact work on the drill bit (2); The impact frequency of the impact piston (3) is determined by the reversing frequency of the pilot control oil circuit (8).

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