A composite impact speed-up drilling tool

Abstract

This invention discloses a composite impact-driven drilling tool, belonging to the field of oil and gas drilling technology. Addressing the problems of poor tool adaptability and asynchronous impact and reversing in existing technologies, this invention proposes a quantitative design method based on the fluid-structure interaction coefficient. The tool's actuating valve assembly includes a coaxially nested inner sleeve and a reversing valve, controlling fluid flow direction through a distribution structure. This invention defines the coupling coefficient between the geometric parameters of the reversing valve and the hydrodynamic parameters. This coefficient is jointly determined by the circumferential impact torque, reversing rotation angle, drilling fluid discharge rate, nozzle pressure drop, and the equivalent hydraulic diameter of the reversing valve, and is controlled within a specific preset range. Through the above quantitative design, the inverse relationship between the reversing angle and the discharge rate is forcibly constrained, achieving efficient synchronization of impact and reversing across the entire discharge range, effectively solving the problems of "idling" or "jamming," and significantly improving rock-breaking efficiency.

Description

Technical Field

[0001] This invention relates to the field of oil and gas drilling technology, and specifically to a composite impact drilling tool for increasing drilling speed. Background Technology

[0002] In deep and ultra-deep well drilling, stick-slip vibration of the drill string is a major cause of decreased mechanical rate of penetration (ROP) and drill string fatigue failure. To suppress stick-slip vibration and assist in rock breaking, composite impact drilling tools, which generate axial hydraulic pulses and circumferential torsional impacts, have become a research hotspot in the field of speed-up drilling.

[0003] Prior art document CN112240160A discloses a composite impact tool, which mainly employs a purely mechanical cam, fork, or rigid limiting rib structure to control the motion coordination between the reversing valve and the impact mechanism. While this "rigid control" logic is structurally simple, it reveals significant poor adaptability to various working conditions in practical applications. Specifically, the reversing angle of such tools ( ) and impact torque ( It is entirely determined by the mechanical structure and cannot be adjusted according to the real-time changes in drilling fluid discharge rate downhole. Dynamic adjustments are made. When the displacement Q fluctuates, the response frequency of the reversing valve and the operating frequency of the impact mechanism are easily out of sync, leading to attenuation of impact energy or even mechanical interference.

[0004] Furthermore, prior art document CN215927249U discloses a jet-type impact tool. Although it utilizes hydrodynamics, its design largely focuses on geometric stacking, lacking consideration of the quantitative relationship between hydraulic parameters, structural dimensions, and motion angles. Existing technologies often neglect the energy distribution relationship between the driving torque required for reversing action and the counter-torque generated by the impact. This leads to the tool "idling" under high displacement conditions because the reversing valve responds too quickly while the impact mechanism has not yet completed energy storage; and under low displacement conditions, insufficient driving energy causes reversing jamming.

[0005] In summary, existing technologies lack a method to reduce drilling fluid discharge ( ), Nozzle pressure drop ( Impact torque () ), reversing angle ( ) and tool geometry ( Therefore, there is an urgent need to develop a composite impact-based drilling tool based on quantitative parameter matching to achieve efficient synergy between axial pulse and circumferential torsional impact under different working conditions. Summary of the Invention

[0006] The purpose of this invention is to provide a composite impact drilling tool for increased drilling speed. Addressing the lack of quantitative design and poor adaptability to operating conditions in existing technologies, this invention proposes a method based on the fluid-structure interaction coefficient. The quantitative design method, by establishing the mathematical relationship between geometric structural parameters and fluid dynamic parameters, solves the technical problem of asynchronous impact and reversal of existing tools under different displacements.

[0007] To achieve the above objectives, the present invention adopts the following technical solution: A composite impact drilling tool for increasing drilling speed includes a housing assembly and an impact mechanism disposed inside, the impact mechanism comprising a static valve assembly and a dynamic valve assembly, characterized in that: The actuated valve assembly includes an inner sleeve and a directional valve coaxially disposed inside the inner sleeve; The lower end of the inner sleeve is connected to a rotary valve, and the lower end of the rotary valve is provided with an impact head; The stationary valve assembly includes a stationary valve fixed to the housing and a lower pressure cap; The reversing valve and the inner sleeve are provided with a flow distribution structure for controlling the flow direction of the fluid. The flow distribution structure is configured to drive the reversing valve to rotate according to the fluid pressure, and at the same time drive the inner sleeve to generate circumferential torsional impact.

[0008] Preferably, the geometric parameters and hydrodynamic parameters of the reversing valve satisfy a preset range for the coupling coefficient α, defined by the following formula:

[0009] in, The circumferential impact torque generated by the inner sleeve; The rotation angle required for the directional valve to complete one directional switching action; This refers to the drilling fluid discharge rate; This represents the pressure drop across the nozzle. This is the equivalent hydraulic diameter of the directional valve.

[0010] Preferably, the coupling coefficient The value range is 0.15 < < 0.35; And the rotation angle of the reversing valve The angle should be 30° to 60° to ensure proper operation at different drilling fluid discharge rates. Under these conditions, the switching frequency of the directional valve is synchronized with the impact frequency of the inner sleeve.

[0011] Preferably, the outer wall of the reversing valve is provided with a high-pressure flow channel and a low-pressure flow channel. The inner wall of the inner sleeve is provided with an inner sleeve pressure transmission channel one and an inner sleeve pressure transmission channel two that cooperate with it. When the reversing valve rotates, the high-pressure fluid drives the inner pressure transmission channel one to move through the high-pressure flow channel of the reversing valve, while the inner pressure transmission channel two is connected to the low-pressure flow channel of the reversing valve to form a pressure relief circuit.

[0012] Preferably, the upper end face of the stationary valve is provided with a fan-shaped distribution of stationary valve reversing valve pressure relief holes and stationary valve outer sleeve pressure relief holes; The pressure relief hole of the stationary valve reversing valve is matched with the flow channel of the reversing valve, and the pressure relief hole of the stationary valve outer sleeve is connected to the outer shell; The pressure relief hole of the stationary valve reversing valve and the pressure relief hole of the stationary valve outer sleeve are 90° apart in the circumferential direction.

[0013] Preferably, the inner sleeve and the reversing valve are fitted together by a guide structure; The guide structure includes a guide protrusion disposed on the outer wall of the reversing valve and a guide groove disposed on the inner wall of the inner sleeve. The guide protrusion can slide circumferentially within the guide groove and restrict axial displacement.

[0014] Preferably, a nozzle is installed at the center of the lower end of the rotary valve, and the diameter of the nozzle is in the range of 8mm to 16mm; The pressure drop generated by the nozzle (13) With displacement Satisfying Relationship:

[0015] And this relationship is incorporated into the coupling coefficient. Calculation in progress.

[0016] Preferably, the housing assembly includes an upper connector and a body, wherein a disc spring is provided inside the body; The upper end of the disc spring abuts against the upper connector, and the lower end abuts against the flow divider sleeve, which is used to compensate for axial wear between the dynamic valve assembly and the static valve assembly.

[0017] Preferably, the first inner sleeve pressure transmission channel and the second inner sleeve pressure transmission channel are symmetrically distributed about the axis of the inner sleeve. The arc length angle of the high-pressure flow channel of the reversing valve is greater than the arc length angle of the inner pressure transmission flow channel to ensure the stability of fluid flow during reversal.

[0018] Preferably, the lower inner wall of the inner sleeve is provided with a radial protrusion, and the upper outer wall of the rotary valve is provided with a rotary valve groove that mates with it. The inner sleeve and the rotary valve are circumferentially fixedly connected by the engagement of the radial protrusion with the groove of the rotary valve, so as to transmit the hydraulic torque that drives the inner sleeve to rotate.

[0019] Compared with the prior art, the composite impact drilling tool provided by the present invention has the following significant advancements and beneficial effects: This invention achieves quantitative coupling between fluid dynamics and mechanical structure, solving the problem of poor adaptability to operating conditions. Existing technologies rely on purely mechanical cam or shift fork structures, resulting in a fixed reversing frequency that cannot adapt to varying downhole displacements. This invention introduces a coupling coefficient... The design method introduces the formula:

[0020] The originally independent "hydraulic parameters ( , ") and structural parameters ( , Establish a corresponding connection so that the tool can adjust based on drilling fluid discharge rate. Automatically match the optimal reversing angle Even with a 20% fluctuation in displacement, this tool can still maintain synchronization between impact and reversal, solving the problems of "impact lag" or "idling" caused by displacement changes in existing technologies.

[0021] This tool optimizes the energy distribution mechanism and significantly improves impact efficiency. This invention achieves this by limiting the coupling coefficient. The range of values ​​for the impact torque is forcibly constrained. With nozzle pressure drop The proportional relationship ensures that hydraulic energy is optimally distributed between "controlling the directional valve's action" and "driving the inner sleeve to generate torsional impact." This avoids insufficient impact energy due to excessively rapid directional switching at high displacements and jamming due to weak drive at low displacements, maximizing the circumferential torsional torque required for rock breaking and effectively increasing the mechanical drilling rate (ROP).

[0022] This tool features a compact internal structure and precise response, improving rock-breaking coordination. By employing a coaxial nested structure of the inner sleeve and the reversing valve, along with a 90° phased pressure relief hole layout on the static valve, and using a calculated reversing angle of 30°~60°, the axial hydraulic pulses and circumferential torsional impacts are strictly synchronized in timing. Compared to the chaotic vibrations in existing technologies, the composite shock waves generated by this tool more effectively assist the drill bit in shearing rock, effectively suppressing drill string stick-slip vibration and extending the service life of the drill string. Attached Figure Description

[0023] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments of this application and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings: Figure 1This is a schematic diagram of a composite impact speed-up drilling tool structure in an embodiment of the present invention; Figure 2 This is the initial working position of the directional valve of the present invention. Figure 1 Internal sectional view of position AA; Figure 3 When the reversing valve of this invention is rotated clockwise to the reversing position, Figure 1 Internal sectional view of position AA; Figure 4 When the inner sleeve of this invention moves counterclockwise to the impact end position, Figure 1 Internal sectional view of position AA; Figure 5 When the reversing valve of this invention rotates counterclockwise to the starting position, Figure 1 Internal sectional view of position AA; Figure 6 This is the present invention. Figure 2 and Figure 3 When at work, Figure 1 Internal sectional view at position CC; Figure 7 This is the present invention. Figure 4 and Figure 5 When at work, Figure 1 Internal sectional view at position CC; Figure 8 This is a top view of the upper pressure cap of the present invention; Figure 9 This is the present invention. Figure 1 Sectional view of the inner sleeve and rotary valve at position BB; Figure 10 This is a top view of the lower pressure cover of the present invention; Figure 11 This is a top view of the static valve of the present invention.

[0024] In the diagram: 1. Upper connector, 2. Body, 3. Diverter sleeve, 4. Upper pressure cap, 5. Outer sleeve, 6. Inner sleeve, 7. Reversing valve, 8. Lower pressure cap, 9. Disc spring, 10. Pressure sleeve, 11. Static valve, 12. Rotary valve, 13. Nozzle, 4-1. Upper pressure cap pressure transmission hole, 5-1. Outer sleeve high-pressure flow channel, 5-2. Outer sleeve pressure relief flow channel, 6-1. Inner sleeve pressure transmission flow channel 1, 6-2. Inner sleeve pressure transmission flow channel 2, 7-1. Reversing valve high-pressure flow channel, 7-2. Reversing valve low-pressure flow channel, 8-1. Lower pressure cap outer sleeve pressure relief hole, 8-2. Lower pressure cap reversing valve pressure relief hole, 11-1. Static valve outer sleeve pressure relief hole, 11-2. Static valve reversing valve pressure relief hole, 11-3. Static valve side hole, 12-1. Rotary valve pressure relief hole, 12-2. Rotary valve groove, 12-3. Rotary valve side hole; In the diagram, H represents the high-pressure area and L represents the low-pressure area. Detailed Implementation

[0025] To more clearly illustrate the overall concept of this application, a detailed explanation is provided below with reference to the accompanying drawings.

[0026] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, this application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0027] Furthermore, it should be understood in the description of this application that the terms "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention.

[0028] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0029] In this application, unless otherwise expressly specified and limited, the "above" or "below" of the second feature can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. In the description of this specification, references to terms such as "an embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described can be combined in any suitable manner in one or more embodiments or examples.

[0030] like Figures 1 to 11 As shown, the composite impact speed-up drilling tool provided by the present invention is mainly composed of a shell assembly, a static valve assembly, and a dynamic valve assembly.

[0031] Example 1: This embodiment details the connection relationships of the various components inside the tool and the specific working process of hydraulic impact.

[0032] like Figure 1 , Figure 6 , Figure 9 As shown, the internal structural assembly relationship of this tool is as follows: Housing assembly: The upper connector 1 is threadedly connected to the body 2, and the outer sleeve 5 is fixed inside the body 2. A disc spring 9 is installed at the bottom of the inner cavity of the body 2. Above the disc spring 9, a pressure sleeve 10 and a diverter sleeve 3 are arranged in sequence. The disc spring 9 provides axial preload to compensate for wear.

[0033] Dynamic valve assembly: The directional valve 7 is located in the center hole of the inner sleeve 6. For example... Figure 6 As shown, the outer wall of the directional valve 7 has an axially extending guide protrusion, and the inner wall of the inner sleeve 6 has a matching guide groove. This structure restricts the axial relative movement between the directional valve 7 and the inner sleeve 6, but allows them to rotate circumferentially under hydraulic pressure.

[0034] Transmission connection: such as Figure 9 As shown, the inner wall of the lower end of the inner sleeve 6 has a radial protrusion, and the outer wall of the upper end of the rotary valve 12 has a corresponding rotary valve groove 12-2. The two are circumferentially fixedly connected by the radial protrusion engaging the rotary valve groove 12-2. The lower end of the rotary valve 12 is connected to the impact head 8, and a nozzle 13 is installed below the impact head 8.

[0035] like Figures 2-7 As shown, the hydraulic impact cycle process during the use of this tool includes the following four steps: Step 1: Initial oil intake and energy storage stage, such as Figure 2 , Figure 6 As shown, drilling fluid enters from the upper connector 1. A portion flows through the diverter sleeve 3 into the outer sleeve 5, forming an annular pulse; the other portion flows through the central channel into the moving valve assembly. At this time, the directional valve 7 is in the initial position. High-pressure fluid H flows through the high-pressure flow channel 7-1 on the outer wall of the directional valve 7 into the inner pressure transmission channel 6-1 on the inner wall of the inner sleeve 6. The high-pressure fluid acts on the blades or piston surface of the inner sleeve 6, generating circumferential hydraulic torque, driving the inner sleeve 6 to begin rotating clockwise. At this time, the inner pressure transmission channel 6-2 on the other side of the inner sleeve 6 connects with the low-pressure flow channel 7-2 of the directional valve 7, leading to the low-pressure zone L, thus achieving oil return.

[0036] Step Two: Impact Generation and Reversal Triggering, such as Figure 3 , Figure 4 , Figure 7 As shown, as the inner sleeve 6 rotates, the rotary valve 12 connected to its lower end rotates synchronously, compressing the internal spring or energy storage chamber to accumulate circumferential potential energy. When the inner sleeve 6 rotates to a set angle (e.g., 45°), the flow channel position of the inner sleeve 6 changes. At this time, the high-pressure fluid acts in the opposite direction on the reversing valve 7 through the distribution structure, driving the reversing valve 7 to overcome friction or spring force and begin to rotate counterclockwise. This action signifies that the impact is about to be released.

[0037] Step 3: Torque release and reset, as follows Figure 5 As shown, after the reversing valve 7 rotates, its flow channel position changes. The original high-pressure oil inlets 7-1 and 6-1 are cut off, and the original low-pressure oil return ports 7-2 and 6-2 become high-pressure oil inlets. Under the reverse action of the hydraulic torque, the inner sleeve 6 rotates rapidly or rebounds under the action of the accumulator spring, generating an instantaneous circumferential torsional impact, and transmitting this torque to the impact head 8 through the rotary valve 12, striking the drill bit. At the same time, the pressure relief hole on the stationary valve 11 completes a switching of one axial pulse.

[0038] Step 4: Cycle closure. After the tool impact is completed, the flow channel returns to a similar state. Figure 2 The state is reversed, but the phase shifts, and the high-pressure liquid re-enters the inner sleeve pressure transmission channel 6-2, driving the inner sleeve 6 to rotate in the opposite direction for the next energy storage, and so on in a cycle.

[0039] Example 2: This embodiment focuses on how to utilize the coupling coefficient defined in claim 2. This is to address the problem of "displacement changes causing shock loss of synchronization" in existing technologies.

[0040] For specific well depth operations, the corresponding indicators are designed as follows: Drilling fluid displacement Set range: 20 ~ 40 L / s (considering pump set fluctuations).

[0041] Nozzle pressure drop Target value: 6 ~ 12 MPa.

[0042] Structural parameters: Based on the tool's outer diameter limitation, the equivalent hydraulic diameter of directional valve 7 is... The initial value is set at 45 mm.

[0043] Target torque : It needs to reach more than 400 N·m to break the hard strata.

[0044] Reversal angle It needs to be calculated according to the formula.

[0045] Based on the coupling coefficient Corresponding formula:

[0046] If designed according to traditional experience, take =90°, substitute into the minimum displacement operating condition ( =20, =6): at this time:

[0047] at this time If the value is too high, it means that at low displacement, the driving energy is insufficient to complete the commutation within 90°, and the tool is very likely to jam.

[0048] In this invention, By controlling the angle within the range of 0.15 to 0.35, the reversal angle can be derived in reverse within this range. :

[0049] Pick =0.25, substituting the parameter, we can see that:

[0050] Change direction angle The design angle is 35°, which conforms to the above. The angle range. Under this reversing angle, the tool operates in two modes: low displacement (20 L / s) and high displacement (40 L / s). In the low displacement mode, the reversing valve can quickly complete a 35° micro-angle rotation, ensuring the reversing frequency keeps pace with the displacement without jamming. In the high displacement mode, due to… in the formula Increase, if Too large an angle will result in too rapid a change of direction and insufficient impact. A 35° angle is recommended. The coefficient ensures that the high-pressure fluid has enough time to act on the inner sleeve 6, thus guaranteeing the stability of the impact torque.

[0051] Therefore, through the quantitative design of this embodiment, the tool can maintain a stable impact frequency and energy in a wide displacement range of 20-40L / s, solving the problem of failure of the comparison file D2 under variable displacement conditions.

[0052] Example 3: like Figure 11 As shown, the static valve 11 serves as a fixed reference component, and the flow channel layout on its upper end face is the basis for achieving precise flow distribution.

[0053] The stationary valve 11 is machined with a stationary valve outer sleeve pressure relief hole 11-1 and a stationary valve directional valve pressure relief hole 11-2. The included angle between the centers of the two in the circumferential direction is 90°. When the moving valve assembly (inner sleeve 6 + directional valve 7) rotates relative to the stationary valve 11, these two pressure relief holes on the stationary valve alternately connect with the internal flow channels of the inner sleeve 6 and the directional valve 7, respectively. This 90° phase difference design, combined with the symmetrical flow channel of the inner sleeve 6, ensures that the switching action between high-pressure oil inlet and low-pressure oil return is crisp and clean during the reversing process, without intermediate stagnation dead zones, effectively preventing the "oil trapping" phenomenon in the hydraulic system and improving the response speed and life of the tool.

[0054] Example 4: During operation, the nozzle 13 at the lower end of the rotary valve 12 has a diameter of 12mm. According to fluid mechanics, the nozzle pressure drop... Combined with coupling coefficient It can be seen that, Located in the denominator. When displacement When it increases instantaneously, The rapid increase in torque causes the denominator in the formula to grow larger, which automatically suppresses the impact torque. The excessive growth of this fluid dynamics, combined with the quantitative design of this invention, allows the tool to maintain stable output characteristics even amidst complex pressure fluctuations at the bottom of the well.

[0055] For any parts not mentioned in this application, existing technologies may be used or referenced.

[0056] The various embodiments in this specification are described in a progressive manner. The same or similar parts between the various embodiments can be referred to each other. Each embodiment focuses on describing the differences from other embodiments.

[0057] The above description is merely an embodiment of this application and is not intended to limit the scope of this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of the claims of this application.

Claims

1. A composite impact drilling tool, comprising a housing assembly and an impact mechanism disposed inside, the impact mechanism comprising a static valve assembly and a dynamic valve assembly, characterized in that: The valve assembly includes an inner sleeve (6) and a directional valve (7) coaxially disposed inside the inner sleeve (6). The lower end of the inner sleeve (6) is connected to a rotary valve (12), and the lower end of the rotary valve (12) is provided with an impact head (8). The static valve assembly includes a static valve (11) fixed to the housing and a lower pressure cap (8). The reversing valve (7) and the inner sleeve (6) are provided with a flow distribution structure for controlling the flow direction of the fluid. The flow distribution structure is configured to drive the reversing valve (7) to rotate according to the fluid pressure and at the same time drive the inner sleeve (6) to generate circumferential torsional impact.

2. The composite impact drilling tool according to claim 1, characterized in that: The geometric parameters and hydrodynamic parameters of the reversing valve (7) satisfy a preset range for the coupling coefficient α, defined by the following formula: , in, The circumferential impact torque generated by the inner sleeve (6); The rotation angle required for the reversing valve (7) to complete one reversing action; This refers to the drilling fluid discharge rate; The pressure drop across the nozzle (13); The equivalent hydraulic diameter of the directional valve (7) is given.

3. The composite impact drilling tool according to claim 2, characterized in that: The coupling coefficient The value range is 0.15 < < 0.35; and the rotation angle of the reversing valve (7) The angle should be 30° to 60° to ensure proper operation at different drilling fluid discharge rates. The switching frequency of the reversing valve (7) is synchronized with the impact frequency of the inner sleeve (6).

4. The composite impact drilling tool according to claim 1, characterized in that: The outer wall of the reversing valve (7) is provided with a high-pressure flow channel (7-1) and a low-pressure flow channel (7-2). The inner wall of the inner sleeve (6) is provided with an inner sleeve pressure transmission channel one (6-1) and an inner sleeve pressure transmission channel two (6-2) that cooperate with it. When the reversing valve (7) rotates, the high-pressure fluid drives the inner sleeve pressure transmission channel one (6-1) to move through the high-pressure flow channel (7-1) of the reversing valve. At the same time, the inner sleeve pressure transmission channel two (6-2) is connected to the low-pressure flow channel (7-2) of the reversing valve to form a pressure relief circuit.

5. The composite impact drilling tool according to claim 4, characterized in that: The upper end face of the stationary valve (11) is provided with a fan-shaped distribution of stationary valve reversing valve pressure relief holes (11-2) and stationary valve outer sleeve pressure relief holes (11-1). The pressure relief hole (11-2) of the static valve reversing valve is matched with the flow channel of the reversing valve (7), and the pressure relief hole (11-1) of the static valve outer sleeve is connected to the outer shell; The pressure relief hole (11-2) of the static valve reversing valve and the pressure relief hole (11-1) of the static valve outer sleeve are 90° apart in the circumferential direction.

6. The composite impact drilling tool according to claim 1, characterized in that: The inner sleeve (6) and the reversing valve (7) are connected by a guide structure; The guide structure includes a guide protrusion disposed on the outer wall of the reversing valve (7) and a guide groove disposed on the inner wall of the inner sleeve (6); The guide protrusion can slide circumferentially within the guide groove and restrict axial displacement.

7. The composite impact drilling tool according to claim 1, characterized in that: A nozzle (13) is installed at the lower center of the rotary valve (12), and the diameter of the nozzle (13) is in the range of 8mm to 16mm. The pressure drop generated by the nozzle (13) With displacement Satisfying Relationship: And this relationship is incorporated into the coupling coefficient. Calculation in progress.

8. The composite impact drilling tool according to claim 1, characterized in that: The housing assembly includes an upper connector (1) and a body (2), and the body (2) is provided with a disc spring (9) inside. The upper end of the disc spring (9) abuts against the upper connector (1), and the lower end abuts against the flow divider sleeve (3), which is used to compensate for axial wear between the dynamic valve assembly and the static valve assembly.

9. A composite impact drilling tool according to claim 4, characterized in that: The inner sleeve pressure transmission channel one (6-1) and the inner sleeve pressure transmission channel two (6-2) are symmetrically distributed about the axis of the inner sleeve (6); The arc length angle of the high-pressure flow channel (7-1) of the reversing valve is greater than the arc length angle of the inner pressure transmission flow channel (6-1) to ensure the stability of fluid flow during reversal.

10. A composite impact drilling tool according to claim 4, characterized in that: The inner wall of the lower end of the inner sleeve (6) is provided with a radial protrusion, and the outer wall of the upper end of the rotary valve (12) is provided with a rotary valve groove (12-2) that cooperates with it. The inner sleeve (6) and the rotary valve (12) are circumferentially fixedly connected by the engagement of the radial protrusion with the rotary valve groove (12-2) to transmit the hydraulic torque that drives the inner sleeve (6) to rotate.

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