State adaptive turbine pulse generator and downhole drill

Abstract

A state-adaptive turbine pulse generator (100) comprises: a pulse generating device (2) comprising a turbine housing (21), a turbine shaft (22) concentrically arranged inside the turbine housing (21), a turbine mechanism sleeved on the turbine shaft (22), and a valve disc mechanism arranged at the lower end of the turbine shaft (22), the turbine mechanism being capable of driving the turbine shaft (22) to rotate under the action of drilling fluid, so that the flow area of the valve disc mechanism periodically changes to generate pressure pulses; an automatic control mechanism (1) for controlling the state of the pulse generating device (2); wherein the automatic control mechanism (1) is configured to enable the turbine shaft (22) to be circumferentially stationary relative to the turbine housing (21) during composite drilling, so that the pulse generating device (2) is in a non-working state, and enable the turbine shaft (22) to rotate relative to the turbine housing (21) under the action of the turbine mechanism during sliding drilling, so that the pulse generating device (2) is in a working state.

Description

[0001] Cross Reference to Related Applications

[0002] This application claims priority to Chinese Patent Application 2021116151302, filed on December 27, 2021, entitled "State Adaptive Turbine Pulse Generator", the entire contents of which are incorporated herein by reference. TECHNICAL FIELD

[0003] The present application belongs to the field of drilling technology, and specifically relates to a state adaptive turbine pulse generator. The present application also relates to a downhole drilling tool. BACKGROUND

[0004] In the drilling of extended reach wells and horizontal wells, because the hole angle is large, most of the weight of the drill string in the large inclination well section is pressed against the well wall, so the friction between the pipe string and the wellbore is large, resulting in drag pressure, increased torque, and discontinuous or limited weight on bit transmitted to the drill bit. It is difficult to advance only with the weight of the straight well section drilling tool, the tool face is difficult to control, the length of the drilled horizontal section is limited, and the rate of penetration is low. By introducing a pressure pulse generation tool and a matching axial vibration generation tool into the downhole pipe string, a pressure pulse is generated by periodically changing the fluid flow area. This pressure pulse acts on the matching axial vibration generation tool, driving the drill string to produce axial peristalsis, reducing the friction coefficient between the pipe string and the well wall during sliding drilling, reducing the friction resistance of the pipe string, eliminating the pipe string drag pressure phenomenon, and improving the weight on bit transmission effect and improving the directional drilling efficiency.

[0005] Chinese Patent Document CN105089501A discloses a hydraulic oscillator, CN106639944A discloses a turbine downhole hydraulic oscillator, CN106761413A discloses a hydraulic oscillator, and Chinese Patent Document CN206280029U discloses a hydraulic oscillator. These hydraulic oscillators all contain a pulse system that uses a short turbine to drive a valve group to generate hydraulic pressure pulses. The turbine hydraulic oscillator described above is always in working condition during directional drilling, but under the condition of composite drilling, the drill string is rotating, and the drill string does not have the phenomenon of drag pressure. At this time, whether the hydraulic oscillator works or not has little effect on drilling operations, but the hydraulic oscillator working will exacerbate the erosion of the valve group. Therefore, the hydraulic oscillator is always in working condition, which will shorten the service life of the pulse system and seriously affect the effect of reducing friction and preventing drag pressure in the later use of the tool. SUMMARY

[0006] Aiming at the technical problems as mentioned above, the present application aims to provide a turbine type pulse generator for downhole tools. The turbine type pulse generator automatically realizes turbine shaft braking or rotation through switching between drilling string rotation and non-rotation state, realizes automatic regulation and control of the working state of the turbine type pulse generator, i.e. the pulse generator stops working under the condition of compound drilling and the pulse generator starts working under the condition of sliding drilling, thereby greatly prolonging the service life of the valve group and significantly improving the effect of reducing the drag of the later stage drilling string and preventing pressure holding in directional well construction.

[0007] To this end, according to a first aspect of the present application, a turbine type pulse generator for downhole drilling tools is provided, comprising: a pulse generating device comprising a turbine housing, a turbine shaft concentrically arranged inside the turbine housing, a turbine mechanism sleeved on the turbine shaft, and a valve disc mechanism arranged at the lower end of the turbine shaft, the turbine mechanism being capable of driving the turbine shaft to rotate relative to the turbine housing under the action of drilling fluid, thereby making the flow area of the valve disc mechanism periodically change to generate pressure pulse; an automatic control mechanism for controlling the state of the pulse generating device; wherein the automatic control mechanism is configured to make the turbine shaft circumferentially stationary relative to the turbine housing to make the pulse generating device in a non-working state when compound drilling, and make the turbine shaft capable of rotating relative to the turbine housing under the action of the turbine mechanism to make the pulse generating device in a working state when sliding drilling.

[0008] In one embodiment, the automatic control mechanism comprises: an outer cylinder fixedly connected to the upper end of the turbine housing; a movable unit arranged in the outer cylinder; and a driving assembly for driving the movable unit to generate axial movement, wherein the turbine shaft has a stop block extending radially inwardly, the driving assembly is configured to make the movable unit move towards the stop block to engage with the stop block when compound drilling, thereby making the turbine shaft circumferentially stationary relative to the turbine housing, and make the movable unit move away from the stop block to disengage from the stop block when sliding drilling, thereby making the turbine shaft rotate relative to the turbine housing.

[0009] In one embodiment, the movable unit comprises a first slider and a second slider arranged axially spaced apart from each other in the outer cylinder, the first slider and the second slider are both arranged to be circumferentially fixed with the outer cylinder and capable of moving axially along the outer cylinder, wherein the lower end of the second slider is provided with a radial outwardly extending brake block extending into the stop block, the driving assembly is arranged between the first slider and the second slider, and is configured to make the first slider and the second slider axially relatively close to make the brake block engage with the stop block when compound drilling, and make the first slider and the second slider axially relatively far away to make the brake block disengage from the stop block when sliding drilling.

[0010] In one embodiment, the stop block is provided with a first engagement surface, and the brake block is provided with a second engagement surface, the first engagement surface being adapted to the second engagement surface so as to engage the brake block with the stop block.

[0011] In one embodiment, the first engagement surface is upstream of the second engagement surface.

[0012] In one embodiment, the drive assembly comprises a leaf spring and a centrifugal block, the centrifugal block being fixed in the axial middle of the leaf spring, and the two ends of the leaf spring being fixedly connected with the first slider and the second slider respectively, the drive assembly being capable of causing the centrifugal block to generate centrifugal force during compound drilling, prompting the leaf spring to deform and expand radially, so as to make the first slider and the second slider axially close to each other.

[0013] In one embodiment, the leaf spring and the centrifugal block are provided with two respectively, and the two leaf springs are radially symmetrically distributed.

[0014] In one embodiment, the first slider and the second slider are circumferentially fixedly connected with the outer cylinder through a spline structure.

[0015] In one embodiment, a limiting step is arranged on the inner wall surface of the outer cylinder, for limiting the position of the second slider axially away from the first slider.

[0016] In one embodiment, the first slider and the second slider are both provided with an axially extending water eye hole for the flow of drilling fluid.

[0017] In one embodiment, the turbine mechanism comprises a stator fixedly connected with the turbine housing and a rotor fixedly connected with the turbine shaft, the rotor being capable of rotating relative to the stator under the action of drilling fluid, thereby driving the turbine shaft to rotate.

[0018] In one embodiment, the valve disc mechanism comprises a moving valve disc and a static valve disc, the moving valve disc being fixedly connected with the turbine shaft, and the static valve disc being fixedly connected with the turbine housing.

[0019] In one embodiment, the static valve disc is provided with a first eccentric hole, and the moving valve disc is provided with a second eccentric hole, the overlapping part of the first eccentric hole and the second eccentric hole periodically changing with the rotation of the moving valve disc, so that the flow area formed by the first eccentric hole and the second eccentric hole of the valve disc mechanism periodically changes.

[0020] In one embodiment, the hole diameter and the eccentric distance of the first eccentric hole and the second eccentric hole are the same.

[0021] In one embodiment, a side wall of the turbine shaft at a lower end of the turbine mechanism is provided with a through hole for communicating a central flow passage inside the turbine shaft with a radial annular space formed between the turbine shaft and the turbine housing.

[0022] In one embodiment, a lower end of the turbine housing is provided with a lower joint which axially abuts against the static valve disc to define an axial position of the static valve disc.

[0023] According to a second aspect of the present application, there is provided a downhole drilling tool comprising:

[0024] a vibration generating tool;

[0025] a steerable motor drilling assembly connected at a lower end of the vibration generating tool; and

[0026] a turbine pulse generator as described above connected between the vibration generating tool and the steerable motor drilling assembly.

[0027] Compared with the prior art, the turbine pulse generator for downhole drilling tools provided by the present application is connected with a vibration generating tool at an upper portion thereof to be added to a steerable motor drilling assembly, so that the drilling tool generates periodic and mild vibration, and the drilling assembly generates axial peristalsis, thereby converting static friction into dynamic friction, significantly reducing the friction between the sliding drilling well wall and the drill pipe, improving the drilling pressure transmission, greatly improving the rate of penetration and the extension capacity of the extended reach well and the horizontal well, and thereby solving the problem of difficult control of the tool face. The turbine pulse generator is automatically controlled by the rotation state of the drill string, and in the composite drilling, the turbine pulse generator stops working; while in the sliding drilling, the turbine pulse generator starts working and generates high-frequency pulses, thereby greatly improving the service life and the drag reduction effect of the state-adaptive turbine pulse generator, and making the directional drilling construction safer and more efficient. BRIEF DESCRIPTION OF DRAWINGS

[0028] The present application will be described below with reference to the accompanying drawings.

[0029] Figure 1 The structure of the turbine pulse generator for downhole drilling tools according to the present application is shown.

[0030] Figure 2 The state of the automatic control mechanism in the turbine pulse generator shown is shown in the composite drilling. Figure 1

[0031] In the present application, all the drawings are schematic drawings for illustrating the principles of the present application only, and are not drawn to scale. ​DETAILED DESCRIPTION

[0032] The present application will be described in detail below with reference to the drawings. The detailed description should not be considered as limiting the application, but rather as a description of certain aspects, features and embodiments of the application.

[0033] Many modifications and variations of the present application described in the specification are possible without departing from the scope or spirit of the application. Other embodiments of the application will be apparent to those skilled in the art from consideration of the specification and practice of the application. The specification and examples are illustrative only.

[0034] For the convenience of understanding, in the present application, the end close to the wellhead is defined as the upper end, the upstream end or similar terms, such as the left end in Figure 1 , while the end away from the wellhead is defined as the lower end, the downstream end or similar terms, such as the right end in Figure 1 . Meanwhile, the direction along the length of the turbine pulse generator is referred to as the longitudinal direction, the axial direction or similar terms, while the direction perpendicular to it is referred to as the transverse direction, the radial direction or similar terms.

[0035] Figure 1 The structure of the turbine pulse generator 100 for downhole drilling tools according to the present application is shown. As shown in Figure 1 , the turbine pulse generator 100 comprises an automatic control mechanism 1 and a pulse generating device 2, the outer cylinder 11 of the automatic control mechanism 1 is fixedly connected with the turbine housing 21 of the pulse generating device 2, and the outer cylinder 11 is at the upper end of the turbine housing 21. The pulse generating device 2 is used to generate pressure pulses, and the automatic control mechanism 1 is used to control the working state of the pulse generating device 2. The automatic control mechanism 1 is configured to enable the pulse generating device 2 to be in a non-working state during composite drilling, and to be in a working state during sliding drilling.

[0036] In order to facilitate installation and disassembly, the outer cylinder 11 and the turbine housing 21 are fixedly connected in a threaded connection manner.

[0037] According to the present application, as shown in Figure 1As shown, the pulse generating device 2 comprises a turbine housing 21, a turbine shaft 22 concentrically arranged inside the turbine housing 21, a turbine mechanism sleeved on the turbine shaft 22, and a valve disc mechanism arranged at the lower end of the turbine shaft 22. The turbine mechanism comprises a stator 23 and a rotor 24, the stator 23 is fixedly connected with the turbine housing 21, and the rotor 24 is fixedly connected with the turbine shaft 22. The stator 23 and the rotor 24 cooperate, the rotor 24 rotates under the driving action of the drilling fluid, and then the rotor 24 drives the turbine shaft 22 to rotate. In order to improve the driving efficiency of the drilling fluid, a plurality of stators 23 and rotors 24 are arranged on the turbine shaft 2. The plurality of stators 23 and rotors 24 jointly drive the turbine shaft 22 to rotate under the action of the drilling fluid.

[0038] In the embodiment, in order to facilitate the flow of the drilling fluid, the turbine shaft 22 is configured as a hollow structure, and a central flow channel extending in the axial direction is arranged inside the turbine shaft 22 for the flow of the drilling fluid.

[0039] According to the present application, the valve disc mechanism comprises a moving valve disc 25 and a static valve disc 26, the moving valve disc 25 is fixedly connected with the end of the turbine shaft 22, and the static valve disc 26 is fixedly connected with the turbine housing 21. The moving valve disc 25 is seated on the upper end surface of the static valve disc 26. The turbine shaft 22 can drive the moving valve disc 25 to rotate, so that the moving valve disc 25 rotates relative to the static valve disc 26.

[0040] In one embodiment, the moving valve disc 25 and the turbine shaft 22 are connected by threads, which facilitates installation and disassembly. In order to ensure smooth operation and reduce the accident rate, the tightening direction of the threads is the same as the rotation direction of the turbine shaft 22. That is, the turbine shaft 22 will not loosen the threads when it rotates.

[0041] The moving valve disc 25 and the static valve disc 26 are respectively machined with first eccentric holes and second eccentric holes of the same hole diameter and the same eccentric distance, the moving valve disc 25 and the static valve disc 26 are arranged in close proximity, and the first eccentric holes and the second eccentric holes are opposite. When the moving valve disc 25 rotates relative to the static valve disc 26, the overlapping area of the first eccentric holes and the second eccentric holes will be periodically changed, thereby changing the flow area of the drilling fluid and generating high-frequency pressure pulses.

[0042] In addition, the lower end of the turbine housing 21 is also provided with a lower joint 27, the lower joint 27 is in axial abutment with the static valve disc 26 to limit the axial position of the static valve disc 26. The lower joint 27 and the turbine housing 21 are connected by threads. The lower joint 27 is used to connect other downhole drilling tools.

[0043] According to the present application, as Figure 1 and Figure 2As shown, the automatic control mechanism 1 comprises an outer cylinder 11, a movable unit arranged in the outer cylinder 11, and a driving assembly 13 for driving the movable unit to generate axial movement. The turbine shaft 22 has a block 221 extending radially inward, and the driving assembly 13 is configured to move the movable unit towards the block 221 to engage with the block 221 during compound drilling, so as to make the turbine shaft 22 circumferentially stationary relative to the turbine housing 21, and move the movable unit away from the block 221 to disengage from the block 221 during sliding drilling, so as to make the turbine shaft 22 rotate relative to the turbine housing 21.

[0044] The movable unit comprises a first slider 12 and a second slider 14 arranged axially apart from each other in the outer cylinder 11, both of which are arranged to be circumferentially fixed with the outer cylinder 11 and axially movable along the outer cylinder 11. The lower end of the second slider 14 is provided with a brake block 141 extending radially outward and extending into the block 221. The driving assembly 13 is arranged between the first slider 12 and the second slider 14. Both ends of the driving assembly 13 are fixedly connected with the first slider 12 and the second slider 14, respectively. The driving assembly 13 is configured to relatively move the first slider 12 and the second slider 14 axially close to each other to engage the brake block 141 with the block 221 during compound drilling, and relatively move the first slider 12 and the second slider 14 axially away from each other to disengage the brake block 141 from the block 221 during sliding drilling.

[0045] According to an embodiment of the present application, the block 221 is provided with a first engagement surface, and the brake block 141 is provided with a second engagement surface, the first engagement surface being adapted to the second engagement surface so as to engage the brake block 141 with the block 221. Preferably, the first engagement surface is upstream of the second engagement surface.

[0046] In an embodiment, the first slider 12 and the second slider 14 are circumferentially fixedly connected with the outer cylinder 11 through spline structures, so that the first slider 12 and the second slider 14 do not rotate relative to the outer cylinder 11, and the first slider 12 and the second slider 14 can only move along the axial direction of the outer cylinder 11 under the action of the driving assembly 13. For example, the first slider 12 and the second slider 14 are respectively provided with external splines, and the positions corresponding to the installation of the first slider 12 and the second slider 14 in the outer cylinder 11 are respectively provided with internal splines, and the first slider 12 and the second slider 14 are respectively adapted to the internal splines of the outer cylinder 11 through the external splines. In addition, a limit step 15 with an end face facing upward is arranged on the inner wall surface of the outer cylinder 11 corresponding to the second slider 14, for limiting the position of the second slider 14 axially away from the first slider 12.

[0047] According to one embodiment of the present application, the driving assembly 13 comprises a leaf spring 131 and a centrifugal block 132. The two ends of the leaf spring 131 are fixedly connected to the first sliding block 12 and the second sliding block 14 respectively. The centrifugal block 132 is fixed to the outer side of the leaf spring 131 and is located at the axial middle position of the leaf spring 131. The centrifugal block 132 can make the leaf spring 131 radially expand by deforming the leaf spring 131 with the centrifugal force, so as to make the first sliding block 12 and the second sliding block 14 axially close to each other.

[0048] In Figure 2 In the embodiment shown, the driving assembly 13 comprises two leaf springs 131 and corresponding two centrifugal blocks 132, and the two leaf springs 131 are arranged in radial symmetry. The two leaf springs 131 and the corresponding centrifugal blocks 132 are both arranged in two numbers to ensure the stable rotation of the outer cylinder 11. In addition, the two leaf springs 131 are arranged in a symmetrical state to ensure the stable rotation of the outer cylinder 11. The centrifugal block 132 is arranged at the central position of the leaf spring 131 to ensure that the leaf spring 131 deforms from the central position under the action of the centrifugal force, thereby improving the stability of the rotation.

[0049] In the specific working process, when the drill pipe composite drilling is performed, the centrifugal block 132 of the driving assembly 13 can generate a centrifugal force under the action of high-speed rotation, promote the leaf spring 131 to generate bending deformation and radially expand, so as to make the first sliding block 12 and the second sliding block 14 axially close to each other, and make the brake block 141 engage with the stop block 221. Figure 2 The engagement state of the brake block 141 and the stop block 221 is shown. At this time, the turbine shaft 22 and the outer cylinder 11 and the turbine housing 21 are relatively stationary in the circumferential direction, and the pulse generating device 2 is in a non-working state. When the drill pipe sliding drilling is performed, the drill pipe does not rotate, the driving assembly 13 does not rotate, the centrifugal block 132 does not generate a centrifugal force, the leaf spring 131 returns to the original state, and the second sliding block 14 is axially pushed downward until the second sliding block 14 is disengaged from the stop block 221. At this time, the turbine shaft 22 rotates under the action of the turbine mechanism and drives the movable valve disc 25 of the valve disc mechanism to rotate, thereby generating a pressure pulse.

[0050] According to the present application, the first sliding block 12 and the second sliding block 14 are both provided with a water eye hole which extends in the axial direction and penetrates the first sliding block 12 and the second sliding block 14. The water eye hole is used for the drilling fluid to flow therethrough.

[0051] The drilling fluid flows through the water holes of the first sliding block 12 and the second sliding block 14, part of which flows into the central flow passage of the turbine shaft 22, and the other part flows through the stator 23 and the rotor 24 to drive the stator 23 and the rotor 24 to rotate relatively. A plurality of through holes 222 are arranged on the side wall of the turbine shaft 22 at the lower end of the turbine mechanism, which are used to communicate the central flow passage of the turbine shaft 22 with the radial annular space formed between the turbine shaft 22 and the turbine housing 21. The drilling fluid flowing between the stator 23 and the rotor 24 drives the rotor 24 to rotate, and finally flows into the central flow passage of the turbine shaft 22 through the radial annular space and the through holes 222. The drilling fluid flowing into the central flow passage flows through the flow passage formed by the first eccentric hole of the moving valve disc 25 and the second eccentric hole of the static valve disc 26. Thus, by changing the aperture of the central flow passage of the turbine shaft 22, the flow rate of the drilling fluid entering between the stator 23 and the rotor 24 can be changed, and the rotating speed of the turbine shaft 22 is changed. The change of the rotating speed also changes the stagger frequency of the eccentric holes on the moving valve disc 25 and the static valve disc 26, and the frequency of the pressure pulse of the drilling fluid passing through the eccentric holes is changed, that is, the frequency of the pressure pulse of the pulse generator is changed to adapt to the requirements of different working conditions on site.

[0052] In actual work process, when the drill pipe is compound drilled, the drill pipe rotates, the outer cylinder 11 drives the centrifugal block 132 to rotate, the generated rotating centrifugal force makes the leaf spring 131 produce bending deformation and expand radially, the deformation of the leaf spring 131 drives the first sliding block 12 and the second sliding block 14 to move axially and close to each other. When the second sliding block 14 moves to a certain position, the brake block 141 on the second sliding block 14 engages with the stop block 221 on the turbine shaft 22, so that the turbine shaft 22 is circumferentially stationary relative to the turbine housing 21. Further, the moving valve disc 25 installed on the turbine shaft 22 also stops rotating, the moving valve disc 25 and the static valve disc 26 do not rotate relatively, and the pulse generator no longer generates pressure pulse. At this time, the pulse generating device 2 is in a non-working state, the erosion of the valve disc mechanism caused by water hammer pressure will disappear, and the service life of the valve disc mechanism is improved. When the drill pipe is sliding drilled, the drill pipe stops rotating, the outer cylinder 11 drives the centrifugal block 132 to stop rotating, the rotating centrifugal force of the centrifugal block 132 disappears, and the leaf spring 131 pushes the first sliding block 12 and the second sliding block 14 to move axially away from each other under the action of the spring force, until the brake block 141 on the second sliding block 14 and the stop block 221 on the turbine shaft 22 are disengaged from each other. The turbine shaft 22 continues to rotate under the action of the drilling fluid, and further drives the moving valve disc 25 to rotate. At this time, the pulse generating device 2 is in a working state, and pressure pulse is generated.

[0053] The turbine pulse generator 100 for downhole drilling tools according to the present application can be applied in extended reach well drilling, horizontal well drilling. The turbine pulse generator 100 is added to the steerable motor drilling tool combination together with the vibration generating tool connected to the upper part of the turbine pulse generator 100, so that the drilling tool generates periodic and mild vibration. In turn, the drilling tool combination generates axial peristalsis, converts static friction into dynamic friction, reduces the friction between the sliding drilling well wall and the drill pipe, improves the drilling pressure transmission, improves the mechanical drilling speed and the extended reach of the extended reach well and horizontal well, and solves the problem of difficult tool face control. At the same time, the state adaptive turbine pulse generator 100 can automatically control the working state of the turbine pulse generating device 2 according to the actual working condition on site through the automatic control mechanism 1. When the drill pipe is composite drilled, the turbine pulse generating device 2 is controlled to be in a non-working state. When the drill pipe is sliding drilled, the turbine pulse generating device 2 is controlled to be in a working state and generates high-frequency pulses, which greatly improves the service life and drag reduction effect of the turbine pulse generator 100, and makes the directional drilling construction safer and more efficient.

[0054] The present application also provides a downhole drilling tool, which comprises a vibration generating tool, a steerable motor drilling tool combination connected to the lower end of the vibration generating tool, and the turbine pulse generator 100 according to the present application connected between the vibration generating tool and the steerable motor drilling tool combination.

[0055] Finally, it should be noted that the above description is only the preferred embodiments of the present application and does not constitute any limitation on the present application. Although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions recorded in the foregoing embodiments or make equivalent replacements to some technical features. Any modification, equivalent replacement, improvement, etc. within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A turbine pulse generator for a downhole drilling tool, comprising: a pulse generating device (2) comprising a turbine housing (21), a turbine shaft (22) concentrically arranged inside the turbine housing, a turbine mechanism sleeved on the turbine shaft, and a valve disc mechanism arranged at a lower end of the turbine shaft, the turbine mechanism being capable of driving the turbine shaft to rotate relative to the turbine housing under the action of drilling fluid, so as to periodically change the flow area of the valve disc mechanism to generate pressure pulses; an automatic control mechanism (1) for controlling the state of the pulse generating device; wherein the automatic control mechanism is configured to enable the turbine shaft to be circumferentially stationary relative to the turbine housing in composite drilling to enable the pulse generating device to be in a non-working state, and enable the turbine shaft to rotate relative to the turbine housing under the action of the turbine mechanism in sliding drilling to enable the pulse generating device to be in a working state.

2. The turbo impulse generator of claim 1, wherein, The automatic control mechanism comprises: an outer cylinder (11) fixedly connected to an upper end of the turbine housing; a movable unit arranged in the outer cylinder; and a driving assembly (13) for driving the movable unit to generate axial movement, wherein the turbine shaft has a stop block (221) extending radially inward, and the driving assembly is configured to enable the movable unit to move towards the stop block to engage with the stop block in composite drilling to enable the turbine shaft to be circumferentially stationary relative to the turbine housing, and enable the movable unit to move away from the stop block to disengage from the stop block in sliding drilling to enable the turbine shaft to rotate relative to the turbine housing.

3. The turbo impulse generator of claim 2, wherein, The movable unit comprises a first slider (12) and a second slider (14) arranged axially spaced apart from each other in the outer cylinder, the first slider and the second slider are both arranged to be circumferentially fixed with the outer cylinder and capable of moving axially along the outer cylinder, wherein a lower end of the second slider is provided with a brake block (141) extending radially outward and extending into the stop block, the driving assembly is arranged between the first slider and the second slider, and is configured to enable the first slider and the second slider to move axially relatively close to each other in composite drilling to enable the brake block to engage with the stop block, and enable the first slider and the second slider to move axially relatively away from each other in sliding drilling to enable the brake block to disengage from the stop block.

4. The turbo impulse generator of claim 3, wherein, The stop block is provided with a first engagement surface, and the brake block is provided with a second engagement surface, the first engagement surface being adapted to the second engagement surface to enable the brake block to engage with the stop block.

5. The turbo impulse generator of claim 4, wherein, The first engagement surface is upstream of the second engagement surface.

6. The turbo impulse generator of claim 3, wherein, The driving assembly comprises a leaf spring (131) and a centrifugal block (132), the centrifugal block being fixed at an axial middle portion of the leaf spring, and both ends of the leaf spring being fixedly connected with the first slider and the second slider respectively, The driving assembly is capable of enabling the centrifugal block to generate centrifugal force in composite drilling to urge the leaf spring to deform and expand radially, so as to enable the first slider and the second slider to move axially relatively close to each other.

7. The turbo impulse generator of claim 6, wherein, The leaf spring and the centrifugal block are respectively provided with two, and the two leaf springs are radially symmetrically distributed.

8. The turbo impulse generator of claim 3, wherein, The first sliding block and the second sliding block are circumferentially fixedly connected with the outer cylinder through a spline structure.

9. The turbo impulse generator according to claim 3 or 8, characterized in that A limiting step (15) is arranged on the inner wall surface of the outer cylinder, for limiting the position of the second sliding block axially away from the first sliding block.

10. The turbo impulse generator of claim 3 or 8, wherein, The first sliding block and the second sliding block are both provided with an axially extending water eye hole for the flow of drilling fluid.

11. The turbo impulse generator of claim 1, wherein, The turbine mechanism comprises a stator (23) fixedly connected with the turbine shell and a rotor (24) fixedly connected with the turbine shaft, and the rotor can rotate relative to the stator under the action of the drilling fluid, thereby driving the turbine shaft to rotate.

12. The turbo impulse generator of claim 1 or 11, wherein, The valve disc mechanism comprises a dynamic valve disc (25) and a static valve disc (26), the dynamic valve disc is fixedly connected with the turbine shaft, and the static valve disc is fixedly connected with the turbine shell.

13. The turbo impulse generator of claim 12, wherein, The first eccentric hole and the second eccentric hole are arranged on the static valve disc and the dynamic valve disc respectively, and the overlapping part of the first eccentric hole and the second eccentric hole periodically changes with the rotation of the dynamic valve disc, so that the flow area formed by the first eccentric hole and the second eccentric hole periodically changes.

14. The turbo impulse generator of claim 13, wherein, The hole diameter and eccentric distance of the first eccentric hole and the second eccentric hole are the same.

15. The turbo impulse generator of claim 1 or 11, wherein, A through hole (222) is arranged on the side wall of the turbine shaft at the lower end of the turbine mechanism, for connecting the central flow channel inside the turbine shaft with the radial annulus formed between the turbine shaft and the turbine shell.

16. The turbo impulse generator of claim 12, wherein, The lower end of the turbine shell (21) is provided with a lower joint (27), which axially abuts against the static valve disc to limit the axial position of the static valve disc.

17. A downhole drilling tool, comprising: a vibration generating tool; a steerable motor drill string assembly connected at a lower end of the vibration generating tool; and a turbine pulse generator according to any one of claims 1 to 16 connected between the vibration generating tool and the steerable motor drill string assembly.

17. A downhole drilling tool, comprising: a vibration generating tool; a steerable motor drill string assembly connected at a lower end of the vibration generating tool; and a turbine pulse generator according to any one of claims 1 to 16 connected between the vibration generating tool and the steerable motor drill string assembly.

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