A torsional impactor for oil and gas drilling

Abstract

The application discloses an oil and gas drilling torsion impactor, and relates to the technical field of rock breaking drilling tools, which comprises a drill string connected with a ground drilling equipment, a fixed cylinder body moving in a well with the drill string, an input shaft rotatably connected with the upper end of the fixed cylinder body through a bearing and fixedly connected with the drill string at the upper portion, a gear transmission group arranged in the fixed cylinder body and fixed on the input shaft, a variable speed transmission assembly rotatably arranged in the fixed cylinder body and engaged with the gear transmission group at the upper portion, a one-way driving device fixedly connected with the lower portion of the input shaft at the upper portion and engaged with the lower portion of the variable speed transmission assembly at the lower portion, and an output shaft rotatably connected with the lower portion of the fixed cylinder body at the upper portion, fixedly connected with the one-way driving device and connected with a drill bit at the lower portion. The application can make the drill bit obtain sufficient instantaneous tangential force by high-frequency pulse torsion impact superposition under periodic speed fluctuation, efficiently inhibit stick-slip, significantly improve the mechanical drilling speed and prolong the service life of the drill bit.

Description

Technical Field

[0001] This invention relates to the field of rock-breaking drilling tools, and more specifically, to an oil and gas drilling torque impactor. Background Technology

[0002] In oil and gas drilling, PDC drill bits are highly susceptible to "stick-slip" when encountering hard and brittle formations. This occurs when the drill bit intermittently sticks due to insufficient torque, and the drill string, after continuous torsional energy storage, suddenly releases it, leading to severe torsional vibration. This not only significantly reduces the rate of penetration (ROP) and accelerates drill bit wear but can also cause drill string fatigue fracture and wellbore quality deterioration. To suppress stick-slip, various torque impactors have been developed in existing technologies, such as hydraulic hammers, turbine hammers, and cam-link hammers. Hydraulic hammers rely on drilling fluid to drive a piston in reciprocating impacts, requiring extremely high mud performance and sealing capabilities, and are prone to erosion failure. Turbine hammers, with their combination of a turbine and an eccentric cam, suffer from rapid cam profile wear and high manufacturing difficulty. Furthermore, most existing torque impactors require complex differential mechanisms or hydraulic control systems to achieve torque superposition, resulting in bulky structures, insufficient reliability, and the impact torque often being transmitted back to the drill string, causing energy waste and impact on surface equipment. Therefore, it is necessary to provide an oil and gas drilling torque impactor to address the problems mentioned in the background technology. Summary of the Invention

[0003] To achieve the above objectives, the present invention provides the following technical solution: an oil and gas drilling torque impactor, comprising:

[0004] The drill string is connected to the surface drilling equipment.

[0005] The fixed cylinder is fixedly installed at the bottom of the drill string and moves with the drill string inside the well.

[0006] The input shaft is rotatably connected to the upper end of the fixed cylinder via a bearing, and the upper part is fixedly connected to the drill string.

[0007] The gear transmission assembly is housed within the fixed cylinder and fixed to the input shaft;

[0008] The speed transmission assembly is rotatably mounted inside the fixed cylinder, and its upper part meshes with the gear transmission assembly;

[0009] A one-way drive device, the upper part of which is fixedly connected to the lower part of the input shaft, and the lower part of which meshes with the lower part of the speed transmission assembly;

[0010] The output shaft is rotatably connected to the lower part of the fixed cylinder at the top and fixedly connected to the one-way drive device. A drill bit is connected to the lower part.

[0011] Furthermore, as a preferred embodiment, the gear transmission assembly is provided with a driving pinion and a driving gear sequentially from top to bottom along the input shaft.

[0012] Furthermore, preferably, the transmission assembly includes:

[0013] The positioning shaft is set parallel to the input shaft and is rotatably mounted inside the fixed cylinder.

[0014] The incomplete large gear is fixed on the positioning shaft and meshes with the drive small gear;

[0015] The incomplete small gear is fixed on the positioning shaft and meshes with the drive large gear;

[0016] The transmission gear is fixed at the lower end of the positioning shaft and meshes with the one-way drive device.

[0017] Furthermore, preferably, the incomplete large gear includes:

[0018] The wheel body is fixed on the positioning shaft;

[0019] It has a toothed section, which is located on the outer rim of the wheel body;

[0020] The smooth section is correspondingly set to the toothed section and fixed on the outer ring of the wheel body;

[0021] The transition section consists of two symmetrically distributed segments, connecting the two ends of the toothed segment and the smooth segment.

[0022] Furthermore, as a preferred embodiment, the incomplete pinion and the incomplete gear have the same structure, but the positions of the toothed section and the smooth section are different.

[0023] Furthermore, preferably, the unidirectional drive device includes:

[0024] The first coupling is fixed at the lower part of the input shaft;

[0025] The first drive shaft is fixedly connected to the first coupling.

[0026] The forward drive assembly is fixedly connected to the first drive shaft at its upper center.

[0027] The second drive shaft is fixedly connected to the forward drive assembly via a second coupling;

[0028] The reverse drive assembly has its upper center fixedly connected to the second drive shaft and its lower center fixedly connected to the output shaft.

[0029] The torque transmission gear is fixed on the outside of the reverse drive assembly and meshes with the transmission assembly.

[0030] Furthermore, preferably, the forward drive component includes:

[0031] The rotating circular surface is fixedly connected to the first drive shaft at its upper center.

[0032] The internal toothed ratchet is located at the upper edge of the rotating circular surface;

[0033] The limit adjustment mechanism is fixed on the rotating circular surface, with its bottom fixedly connected to the first transmission shaft and its top corresponding to the internal tooth ratchet.

[0034] The reverse drive assembly has the same structure as the forward drive assembly, except that the locking directions of the internal toothed ratchet and the limit adjustment mechanism are opposite.

[0035] Furthermore, preferably, the limit adjustment mechanism includes:

[0036] The fixed slide is fixed to the upper part of the rotating circular surface;

[0037] The locking block is slidably set on a fixed slide rail, with its top inclined surface corresponding to the internal toothed ratchet.

[0038] A reset spring connects the bottom of the locking block to the first drive shaft.

[0039] Compared with the prior art, the beneficial effects of the present invention are:

[0040] In this invention, by setting the driving pinion and driving gear to alternately mesh with the incomplete large gear and the incomplete pinion with toothed segments having different phases, the positioning shaft generates periodic "slow-fast" speed fluctuations, which are then transmitted proportionally to the internal tooth ratchet of the reverse drive component via the transmission gear, thereby obtaining a high-frequency stable pulse torque source.

[0041] By setting both the forward drive component and the reverse drive component to use a limit adjustment mechanism in conjunction with an internal tooth ratchet, and making their locking directions opposite, when the reverse drive component locks due to high speed and generates impact torque, the forward drive component automatically slips, so that the impact torque is only superimposed on the output shaft and is not transmitted to the drill string in the reverse direction, thus avoiding energy waste and equipment impact.

[0042] By setting a limit adjustment mechanism on the rotating circular surface with a locking block that can slide along a fixed slide, a return spring and an internal toothed ratchet tooth groove, reliable unidirectional torque transmission is achieved by using the inclined plane self-locking principle. At the same time, when the overrun occurs, the tooth tip pushes the locking block to compress the spring to complete the quick disengagement, ensuring the response sensitivity and long-term durability under high frequency switching.

[0043] By continuously transmitting a portion of the torque from the input shaft to the output shaft via the forward drive assembly, and simultaneously converting another portion of the torque into high-frequency pulses via the gear transmission group and speed change transmission assembly, which are then superimposed onto the same output shaft via the reverse drive assembly, the parallel drive of the basic continuous torque and the pulse impact torque is achieved. This ensures that the drill bit receives multiple instantaneous high tangential forces in each rotation cycle, fundamentally disrupting the conditions for stick-slip formation and significantly improving the mechanical drilling speed and drill bit life. Attached Figure Description

[0044] Figure 1 A schematic diagram of the overall structure of an oil and gas drilling torque impactor;

[0045] Figure 2 A schematic diagram of the planar structure of an oil and gas drilling torsion impactor;

[0046] Figure 3 This is a schematic diagram of the gear transmission assembly and speed change transmission components.

[0047] Figure 4 This is a bottom view of the transmission assembly;

[0048] Figure 5 This is a top view of the transmission assembly;

[0049] Figure 6 This is a schematic diagram of a unidirectional drive device.

[0050] Figure 7 This is a schematic diagram of the forward drive component structure;

[0051] Figure 8 This is a schematic diagram of the reverse drive component and the limit adjustment mechanism.

[0052] In the diagram: 1. Drill string; 2. Fixed cylinder; 3. Input shaft; 4. Gear transmission assembly; 5. Speed ​​transmission component; 6. One-way drive device; 7. Output shaft; 41. Drive pinion; 42. Drive gear; 51. Positioning shaft; 52. Incomplete gear; 53. Incomplete pinion; 54. Transmission gear; 61. First coupling; 62. First transmission shaft; 63. Forward drive component; 64. Second coupling; 65. Second transmission shaft; 66. Reverse drive component; 67. Torque transmission gear; 521. Wheel body; 522. Toothed section; 523. Smooth section; 524. Transition section; 631. Rotating circular surface; 632. Internal toothed ratchet; 633. Limit adjustment mechanism; 6331. Fixed slide; 6332. Locking block; 6333. Return spring. Detailed Implementation

[0053] Please see Figures 1 to 8 In this embodiment of the invention, an oil and gas drilling torque impactor includes:

[0054] Drill string 1 is connected to the ground drilling equipment;

[0055] The fixed cylinder 2 is fixedly installed at the lower part of the drill string 1 and moves with the drill string 1 inside the well.

[0056] The input shaft 3 is rotatably connected to the upper end of the fixed cylinder 2 via a bearing, and its upper part is fixedly connected to the drill string 1;

[0057] The gear transmission assembly 4 is installed inside the fixed cylinder 2 and fixed on the input shaft 3;

[0058] The speed transmission assembly 5 is rotatably mounted inside the fixed cylinder 2, and its upper part meshes with the gear transmission assembly 4;

[0059] The upper part of the one-way drive device 6 is fixedly connected to the lower part of the input shaft 3, and the lower part is engaged with the lower part of the speed transmission assembly 5.

[0060] The output shaft 7 is rotatably connected to the lower part of the fixed cylinder 2 at its upper part and is fixedly connected to the one-way drive device 6. A drill bit is connected to the lower part of the shaft.

[0061] In this embodiment, the gear transmission group 4 is provided with a driving pinion 41 and a driving gear 42 sequentially from top to bottom along the input shaft 3.

[0062] In other words, during drilling operations, the input shaft 3 rotates clockwise at a constant speed, causing the driving pinion 41 and driving gear 42 to rotate coaxially, at the same speed, and in the same direction. The two gears have the same module but different numbers of teeth (the driving pinion 41 has fewer teeth, and the driving gear 42 has more teeth). They are used to mesh with the transmission assembly 5. Using two fixed-number-of-teeth gears arranged vertically, they mesh successively with two gears in the transmission assembly 5 with different transmission ratios during the rotation of the input shaft 3, producing periodic speed changes. Furthermore, the driving pinion 41 and driving gear 42 are fixedly connected to the input shaft 3, with no relative motion. This design is simple, transmits high torque, and is not prone to failure. It should be noted that oil and gas drilling generally proceeds vertically downwards. Figure 2 For example, the upper part corresponds to the right end, and the lower part corresponds to the left end. The fixed cylinder 2 is limited by an external limiting structure (such as a guide key that cooperates with the casing or an upper fixed shaft) so that it can only move along the wellbore axis and cannot rotate around its own axis.

[0063] In this embodiment, the transmission assembly 5 includes:

[0064] The positioning shaft 51 is arranged parallel to the input shaft 3 and is rotatably mounted inside the fixed cylinder 2;

[0065] The incomplete large gear 52 is fixed on the positioning shaft 51 and meshes with the driving small gear 41;

[0066] The incomplete small gear 53 is fixed on the positioning shaft 51 and meshes with the drive large gear 42;

[0067] The transmission gear 54 is fixed at the lower end of the positioning shaft 51 and meshes with the one-way drive device 6.

[0068] In other words, the positioning shaft 51 is mounted in the fixed cylinder 2 through bearings, parallel to the input shaft 3. When the input shaft 3 rotates, the driving pinion 41 meshes with the incomplete large gear 52, and at the same time, the driving large gear 42 meshes with the incomplete pinion 53. Due to the structural characteristics of the incomplete gears, the two meshing pairs do not mesh continuously at the same time, but alternately. The rotational speed of the positioning shaft 51 is determined by the gear pair currently in meshing. When the driving pinion 41 meshes with the incomplete large gear 52, the rotational speed of the positioning shaft 51 is slower; when the driving large gear 42 meshes with the incomplete pinion 53, the rotational speed of the positioning shaft 51 is faster. The transmission gear 54 at the lower end of the positioning shaft 51 rotates at the same speed as the positioning shaft 51 and meshes with the one-way drive device 6, transmitting the periodically changing rotational speed to the one-way drive device 6.

[0069] In this embodiment, the incomplete large gear 52 includes:

[0070] Wheel body 521 is fixed on positioning shaft 51;

[0071] A toothed section 522 is provided on the outer ring of the wheel body 521;

[0072] The smooth section 523 is provided in correspondence with the toothed section 522 and is fixed on the outer ring of the wheel body 521;

[0073] The transition section 524 has two symmetrically distributed sections, connecting the two ends of the toothed section 522 and the smooth section 523.

[0074] In this embodiment, the incomplete pinion 53 and the incomplete gear 52 have the same structure, but the toothed section 522 and the smooth section 523 are in different positions.

[0075] In other words, the incomplete large gear 52 rotates with the positioning shaft 51. Its outer ring is divided into a toothed section 522, a smooth section 523, and two transition sections 524. When the toothed section 522 engages with the driving pinion 41, power is transmitted normally, and the positioning shaft 51 is driven to rotate. When the smooth section 523 rotates to the position of the driving pinion 41, the two are not in contact, the driving pinion 41 rotates freely, and the incomplete large gear 52 is not driven by the gear pair. At the boundary between engagement and disengagement, the transition section 524 adopts an arc transition. This allows the gear teeth to smoothly enter and disengage, avoiding impact and jamming. Since the incomplete pinion 53 and the incomplete large gear 52 are fixed on the same positioning shaft 51, and the toothed section 522 and the smooth section 523 of the two are in different positions, when the incomplete large gear 52 is engaged in the toothed section 522, the incomplete pinion 53 is idling in the smooth section 523, and vice versa. This achieves the alternation of the engagement of the driving pinion 41 and the incomplete large gear 52 with the engagement of the driving large gear 42 and the incomplete pinion 53.

[0076] In a preferred embodiment, when the driving pinion 41 meshes with the incomplete large gear 52, the driving large gear 42 is exactly opposite to the smooth section 523 of the incomplete pinion 53; when the driving large gear 42 meshes with the toothed section 522 of the incomplete pinion 53, the driving pinion 41 is exactly opposite to the smooth section 523 of the incomplete large gear 52. During the rotation of the input shaft 3, the positioning shaft 51 is first driven at a slower speed (larger transmission ratio) for a period of time, and then driven at a faster speed (smaller transmission ratio) for a period of time, forming a periodic speed fluctuation of "slow-fast-slow-fast".

[0077] In this embodiment, the unidirectional drive device 6 includes:

[0078] The first coupling 61 is fixed to the lower part of the input shaft 3;

[0079] The first drive shaft 62 is fixedly connected to the first coupling 61;

[0080] The upper center of the forward drive assembly 63 is fixedly connected to the first drive shaft 62.

[0081] The second drive shaft 65 is fixedly connected to the forward drive assembly 63 via the second coupling 64;

[0082] The reverse drive assembly 66 has its upper center fixedly connected to the second drive shaft 65 and its lower center fixedly connected to the output shaft 7;

[0083] The torque transmission gear 67 is fixed on the outside of the reverse drive assembly 66 and meshes with the speed transmission assembly 5.

[0084] In other words, the continuous power transmission path is as follows: under the action of the drill string 1, the first transmission shaft 62 is driven to rotate through the input shaft 3 and the first coupling 61, which in turn drives the forward drive assembly 63 to rotate. The forward drive assembly 63 drives the second coupling 64 and the second transmission shaft 65 to rotate, which in turn drives the reverse drive assembly 66 to rotate. Then, the drill bit is driven to rotate and drill through the output shaft 7. This path is always driven by the input shaft 3, providing basic continuous torque. The pulse power transmission path is as follows: the transmission gear 54 of the speed transmission assembly 5 drives the torque transmission gear 67 to rotate. The torque transmission gear 67 is fixed on the reverse drive assembly (66), thereby applying periodic speed to the reverse drive assembly 66 to generate additional pulse torque. The forward drive assembly 63 and the reverse drive assembly 66 are in the "torque transmission" or "overspeed slippage" state respectively under a specific relative speed difference. The meshing of the transmission gear 54 and the torque transmission gear 67 is 1:1, so that the angular velocity fluctuation of the positioning shaft 51 is directly and proportionally transmitted to the reverse drive assembly 66, and the control is precise.

[0085] In this embodiment, the forward drive component 63 includes:

[0086] Rotate the circular surface 631, and fix its upper center to the first drive shaft 62;

[0087] The internal toothed ratchet 632 is rotatably located at the upper edge of the rotating circular surface 631;

[0088] The limit adjustment mechanism 633 is fixed on the rotating circular surface 631, with its bottom fixedly connected to the first transmission shaft 62 and its top corresponding to the internal gear ratchet 632.

[0089] The reverse drive assembly 66 has the same structure as the forward drive assembly 63, wherein the locking directions of the internal tooth ratchet 632 and the limit adjustment mechanism 633 are opposite.

[0090] In a preferred embodiment, the locking direction of the forward drive assembly 63 is as follows: its internal ratchet 632 and the limit adjustment mechanism 633 can only transmit clockwise relative motion. That is, when the rotating surface 631 has a clockwise rotation tendency relative to the internal ratchet 632, the limit adjustment mechanism 633 pushes into the tooth groove of the internal ratchet 632, and the two are locked. The torque is transmitted from the rotating surface 631 to the internal ratchet 632. When the internal ratchet 632 has a clockwise rotation tendency relative to the rotating surface 631, the limit adjustment mechanism 633 pushes back, the two slip, and no torque is transmitted.

[0091] In a preferred embodiment, the locking direction of the reverse drive assembly 66 is opposite to that of the forward drive assembly 63, i.e., it can only transmit counterclockwise relative motion. However, since all rotations during drilling are clockwise, the actual locking condition of the reverse drive assembly 66 is as follows: when the clockwise rotation speed of the internal ratchet 632 is greater than the clockwise rotation speed of the rotating surface 631, the reverse drive assembly 66 is locked, generating an additional clockwise impact torque transmitted to the output shaft 7; when the rotation speed of the internal ratchet 632 is less than or equal to the rotation speed of the rotating surface 631, the relative motion between the two is clockwise or stationary, and the reverse drive assembly 66 slips.

[0092] In other words, when the input shaft 3 continuously rotates, and the driving pinion 41 and the partially engaged large gear 52 mesh, the transmission ratio between the input shaft 3 and the positioning shaft 51 increases, thus slowing down the rotational speed of the positioning shaft 51. Under the transmission of the transmission gear 54 and the torque transmission gear 67, the rotational speed of the internal ratchet 632 in the reverse drive assembly 66 is less than the rotational speed of the rotating surface 631. Consequently, the limit adjustment mechanism 633 on the rotating surface 631 and the internal ratchet 632 are in a slipping state, and the output shaft 7 maintains a normal rotational speed. When the driving large gear 42 and the partially engaged small gear 53 mesh, the transmission ratio between the input shaft 3 and the positioning shaft 51 decreases, thus speeding up the rotational speed of the positioning shaft 51. Under the transmission of the transmission gear 54 and the torque transmission gear 67, the internal ratchet 632 in the reverse drive assembly 66... The rotational speed is greater than that of the rotating circular surface 631, which causes the limit adjustment mechanism 633 and the internal gear ratchet 632 on the rotating circular surface 631 to be locked, generating an instantaneous torque to accelerate the output shaft 7. At the same time, the rotational speed of the output shaft 7 increases, which in turn drives the second transmission shaft 65 to increase its speed through the rotating circular surface 631. This causes the internal gear ratchet 632 in the forward drive assembly 63 to rotate at a speed greater than that of the rotating circular surface 631 and the first transmission shaft 62. At this time, the internal gear ratchet 632 and the limit adjustment mechanism 633 on the rotating circular surface 631 are in a slipping state, which does not affect the normal rotational input of the input shaft 3. When switching back to the engagement of the drive pinion 41 and the incompletely meshed large gear 52, the input shaft 3 controls the forward drive assembly 63 to take over again, and the input shaft 3 drives the output shaft 7 and the drill bit to drill again.

[0093] In this embodiment, the limit adjustment mechanism 633 includes:

[0094] The fixed slide 6331 is fixed to the upper part of the rotating circular surface 631;

[0095] The locking block 6332 is slidably set on the fixed slide rail 6331, and its top inclined surface corresponds to the internal tooth ratchet 632.

[0096] The return spring 6333 connects the bottom of the connecting block 6332 to the first drive shaft 62.

[0097] In other words, the locking block 6332 can move radially along the fixed slide 6331, and the return spring 6333 always pushes the locking block 6332 towards the tooth groove of the internal ratchet 632. In the forward drive assembly 63, in the engaged state: when the rotating circular surface 631 has a clockwise rotation tendency relative to the internal ratchet 632, the tooth groove of the internal ratchet 632 cooperates with the inclined surface at the top of the locking block 6332, and the locking block 6332 is pushed into the tooth groove. Due to the self-locking of the inclined surface, the locking block 6332 cannot be disengaged. Locking both components transmits torque. In the overrunning state: when the internal ratchet 632 tends to rotate clockwise relative to the rotating circular surface 631, the tooth tip of the internal ratchet 632 will push the inclined surface of the locking block 6332, causing the locking block 6332 to compress the return spring 6333 and move outward along the fixed slide 6331, thereby disengaging from the tooth groove. The two components slip, and the preload of the return spring 6333 is calculated to ensure that the locking block 6332 can reliably engage and disengage in time during normal torque transmission, avoiding jamming.

[0098] In practice, the drill string 1 first drives the input shaft 3 to rotate clockwise at a constant speed. The input shaft 3 drives the rotating surface 631 of the forward drive assembly 63 to rotate clockwise through the first coupling 61 and the first transmission shaft 62. On the other hand, it drives the driving pinion 41 and the driving gear 42 on it to rotate synchronously. Since the fixed cylinder 2 is restricted from rotating, the positioning shaft 51 is installed parallel to the input shaft 3 inside the fixed cylinder 2. The incomplete large gear 52 and the incomplete small gear 53 fixed on it have tooth segments 522 in different positions, so that the driving pinion 41 and the incomplete small gear 53 are in different positions. When the toothed section 522 of the large gear 52 meshes, the driving large gear 42 is exactly opposite to the smooth section 523 of the incomplete small gear 53. At this time, the transmission ratio increases, and the positioning shaft 51 rotates at a slower speed. Conversely, when the driving large gear 42 meshes with the toothed section 522 of the incomplete small gear 53, the driving small gear 41 is opposite to the smooth section 523 of the incomplete large gear 52. The transmission ratio decreases, and the positioning shaft 51 rotates at a faster speed. Thus, the positioning shaft 51 forms a periodic speed fluctuation of "slow-fast-slow-fast". This fluctuation is transmitted through the transmission gear 54 at the lower end of the positioning shaft 51. The torque is transmitted (1:1 meshing) to the torque delivery gear 67 fixed on the outside of the reverse drive assembly 66, which in turn drives the internal toothed ratchet 632 of the reverse drive assembly 66 to produce the same periodic speed change. At the same time, the continuous torque transmitted from the input shaft 3 to the forward drive assembly 63 drives the rotating surface 631 of the reverse drive assembly 66 and the output shaft 7 through the second coupling 64 and the second transmission shaft 65, so that the drill bit obtains the basic continuous cutting torque. The limit adjustment mechanism 633 of the forward drive assembly 63 is designed to transmit only clockwise relative motion (i.e., rotation). When the moving circular surface 631 is faster than the internal tooth ratchet 632, it locks. However, the limit adjustment mechanism 633 of the reverse drive assembly 66 locks in the opposite direction and can only transmit counterclockwise relative motion (i.e., when the internal tooth ratchet 632 is faster than the rotating circular surface 631, it locks). Therefore, when the positioning shaft 51 is in the slow stage, the speed of the internal tooth ratchet 632 of the reverse drive assembly 66 is less than the speed of its rotating circular surface 631. The relative motion between the two is clockwise, and the reverse drive assembly 66 is in a slipping state and does not generate additional torque. The drill bit is only continuously driven by the input shaft 3 through the forward drive assembly 63.When the positioning shaft 51 switches to the rapid phase and the internal ratchet 632 rotates at a speed greater than that of its rotating surface 631, their relative motion becomes counterclockwise. The reverse drive assembly 66 locks, and the internal ratchet 632 transmits the instantaneous impact torque to the rotating surface 631 through the locking block 6332, thereby applying a positive pulse torque to the output shaft 7, giving the drill bit instantaneous acceleration. This acceleration is transmitted through the second drive shaft 65 and the internal ratchet 632 of the forward drive assembly 63. Since the internal ratchet 632 of the forward drive assembly 63 rotates at a speed greater than that of its rotating surface 631 (driven by the input shaft 3), the relative motion between the two becomes counterclockwise. The forward drive assembly 63 locks clockwise (i.e., the rotating surface 631 locks only when it rotates faster than the internal gear ratchet 632), so the forward drive assembly 63 automatically slips, preventing the impact torque from being transmitted back to the input shaft 3 and the drill string 1. Then, when the positioning shaft 51 returns to a slow speed, the reverse drive assembly 66 slips again, and the forward drive assembly 63 re-engages, allowing the input shaft 3 to continue driving the output shaft 7 stably. This cycle repeats, generating multiple high-frequency unidirectional torque pulses within each rotation cycle of the input shaft 3, ensuring the drill bit always receives sufficient instantaneous tangential force and effectively suppressing stick-slip.

[0099] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A torsion impactor for oil and gas drilling, characterized in that: include: Drill string (1) is connected to the ground drilling equipment; The fixed cylinder (2) is fixedly installed at the lower part of the drill string (1) and moves with the drill string (1) inside the well. The input shaft (3) is rotatably connected to the upper end of the fixed cylinder (2) via a bearing, and its upper part is fixedly connected to the drill string (1); The gear transmission assembly (4) is set inside the fixed cylinder (2) and fixed on the input shaft (3); The speed transmission assembly (5) is rotatably installed inside the fixed cylinder (2), and its upper part meshes with the gear transmission assembly (4); The upper part of the one-way drive device (6) is fixedly connected to the lower part of the input shaft (3), and the lower part is engaged with the lower part of the speed transmission assembly (5); The output shaft (7) is rotatably connected to the lower part of the fixed cylinder (2) and fixedly connected to the one-way drive device (6). A drill bit is connected to the lower part.

2. The torsion impactor for oil and gas drilling according to claim 1, characterized in that: The gear transmission assembly (4) is provided with a driving pinion (41) and a driving gear (42) in sequence from top to bottom along the input shaft (3).

3. The oil and gas drilling torque impactor according to claim 2, characterized in that: The transmission assembly (5) includes: The positioning shaft (51) is set parallel to the input shaft (3) and is rotatably set inside the fixed cylinder (2); The incomplete large gear (52) is fixed on the positioning shaft (51) and meshes with the driving small gear (41); The incomplete pinion (53) is fixed on the positioning shaft (51) and meshes with the drive gear (42); The transmission gear (54) is fixed at the lower end of the positioning shaft (51) and meshes with the one-way drive device (6).

4. The oil and gas drilling torque impactor according to claim 3, characterized in that: The incomplete large gear (52) includes: The wheel body (521) is fixed on the positioning shaft (51); A toothed section (522) is provided on the outer ring of the wheel body (521); The smooth section (523) is provided in correspondence with the toothed section (522) and is fixed on the outer ring of the wheel body (521); The transition section (524) is symmetrically distributed in two sections, connecting the two ends of the toothed section (522) and the smooth section (523).

5. The oil and gas drilling torque impactor according to claim 4, characterized in that: The incomplete pinion (53) and the incomplete gear (52) have the same structure, but the toothed section (522) and the smooth section (523) are in different positions.

6. The torsion impactor for oil and gas drilling according to claim 1, characterized in that: The unidirectional drive device (6) includes: The first coupling (61) is fixed to the lower part of the input shaft (3); The first drive shaft (62) is fixedly connected to the first coupling (61); The forward drive assembly (63) is fixedly connected to the first drive shaft (62) at its upper center; The second drive shaft (65) is fixedly connected to the forward drive assembly (63) via the second coupling (64); The reverse drive assembly (66) has its upper center fixedly connected to the second drive shaft (65) and its lower center fixedly connected to the output shaft (7); The torque transmission gear (67) is fixed on the outside of the reverse drive assembly (66) and meshes with the transmission assembly (5).

7. The oil and gas drilling torque impactor according to claim 6, characterized in that: The forward drive component (63) includes: Rotate the circular surface (631), and fix the upper center to the first transmission shaft (62); An internal toothed ratchet (632) is rotatably located at the upper edge of the rotating circular surface (631); The limit adjustment mechanism (633) is fixed on the rotating circular surface (631), with its bottom fixedly connected to the first transmission shaft (62) and its top corresponding to the internal tooth ratchet (632); The reverse drive assembly (66) has the same structure as the forward drive assembly (63), wherein the locking directions of the internal tooth ratchet (632) and the limit adjustment mechanism (633) are opposite.

8. The oil and gas drilling torque impactor according to claim 7, characterized in that: The limit adjustment mechanism (633) includes: A fixed slide (6331) is fixed on the upper part of the rotating circular surface (631); The locking block (6332) is slidably set on the fixed slide rail (6331), and its top inclined surface corresponds to the internal tooth ratchet (632); The return spring (6333) connects the bottom of the connecting block (6332) and the first drive shaft (62).

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