A face gear transmission-based hydraulic vibration hammer torque adjuster and torque adjusting method

Abstract

The present application relates to the field of engineering machinery, and specifically relates to a hydraulic vibration hammer torque adjuster based on face gear transmission and a torque adjusting method, the hydraulic vibration hammer torque adjuster comprising a central shaft, a transmission assembly, a torque adjusting assembly and a driving assembly, the transmission assembly comprising a planet carrier and a planet wheel, the planet carrier being fixedly connected to the central shaft, and the planet wheel being rotatably connected to the planet carrier, the torque adjusting assembly comprising a first face gear and a second face gear, both of which are rotatably connected to the central shaft and have opposite tooth surfaces, the planet wheel being meshed with the two face gears, the axes of the two face gears being perpendicular to the axis of the planet wheel, the driving assembly comprising a first driving unit and a second driving unit, the first driving unit driving the central shaft, and the second driving unit driving the first face gear or the second face gear to make the two face gears rotate in opposite directions. The present application utilizes the characteristic of face gears being insensitive to axial errors to solve the failure of the tooth surface of bevel gears, and realizes the adjustment of eccentric torque after vibration elimination in the starting stage.

Description

Technical Field

[0001] This invention relates to the field of engineering machinery technology, and in particular to a torque adjuster and method for a hydraulic vibratory hammer based on face gear transmission. Background Technology

[0002] Hydraulic vibratory hammers are core equipment in pile foundation construction, widely used in building engineering, bridge construction, port and dock construction, and urban underground space development. Their working principle is as follows: a hydraulic motor drives an eccentric block to rotate at high speed, generating periodic centrifugal force, which forms an excitation force along the pile's axial direction. This causes a "liquefaction" effect in the soil surrounding the pile, significantly reducing pile-soil friction resistance and achieving efficient pile driving. In actual construction, geological conditions are complex and varied, pile specifications differ, and the amplitude requirements for the excitation force vary significantly under different working conditions—a small excitation force is needed in soft soil layers to prevent the pile from sinking too quickly and causing displacement, while a large excitation force is needed in hard soil or rock layers to overcome the pile driving resistance. Therefore, hydraulic vibratory hammers must be equipped with a torque adjuster to adjust the relative phase angle of the eccentric block according to real-time working conditions, changing the magnitude of the eccentric torque and achieving flexible matching of the excitation force.

[0003] At present, the torque adjustment mechanism of hydraulic vibratory hammer mainly adopts the following technical routes: (1) bevel gear differential transmission scheme, which uses bevel gear pairs to realize power transmission and phase adjustment between intersecting shafts; (2) multi-stage cylindrical gear planetary transmission scheme, which drives the eccentric block after reducing speed and increasing torque through multi-stage gears; (3) synchronous belt transmission scheme, which realizes stepless adjustment through belt transmission.

[0004] However, the above-mentioned existing technologies all have different degrees of defects: (1) In the bevel gear differential scheme, the bevel gear pair is extremely sensitive to axial installation error, while the hydraulic vibratory hammer is in a harsh environment of high frequency strong vibration and large impact when it is working. The excitation acceleration can reach more than 10g, which leads to frequent axial movement of the bevel gear, a sharp decrease in meshing overlap, and a 2 to 3 times increase in the peak value of tooth surface contact stress. The problems of tooth surface pitting and scuffing failure are prominent, resulting in poor reliability and short service life; (2) Although the multi-stage cylindrical gear scheme has a reasonable load-bearing capacity, the transmission chain is long and there are many parts. This leads to an excessively large axial dimension of the torque adjuster, making it difficult to arrange in the limited internal space of the vibratory hammer. Furthermore, the increased weight significantly degrades the dynamic response characteristics of the vibratory hammer. (3) Although the synchronous belt drive scheme can achieve a certain degree of stepless adjustment, its load-bearing capacity is limited. Under heavy load conditions, it is prone to problems such as overload, slippage, and tooth skipping. Moreover, the performance of the rubber material degrades significantly in a wide temperature range of -20℃ to +60℃, which cannot meet the reliable use requirements of large hydraulic vibratory hammers (such as the VM32.2 type, with a rated torque of 1463Nm).

[0005] Furthermore, none of the above solutions can adjust the eccentric torque in real time during the operation of the vibratory hammer—the position of the eccentric block must be adjusted when the machine is stopped. This not only reduces construction efficiency, but more seriously, the vibratory hammer needs to accelerate from zero speed to the working speed every time it is started. Its excitation frequency will inevitably cross the natural frequency of the crane system during the acceleration process, causing violent resonance and causing the boom to swing significantly. In severe cases, it may lead to equipment overturning accidents. Summary of the Invention

[0006] The purpose of this invention is to provide a torque adjuster and adjustment method for a hydraulic vibratory hammer based on face gear transmission, in order to solve the problem that the existing hydraulic vibratory hammer torque adjuster is extremely sensitive to axial installation errors under strong vibration conditions, resulting in poor meshing stability, easy failure of tooth surfaces, and inability to meet the reliability requirements of heavy-duty high-frequency operation of large vibratory hammers.

[0007] To achieve the above objectives, the present invention adopts the following technical solution: This invention discloses a hydraulic vibratory hammer torque adjuster based on face gear transmission, comprising: Central axis; The transmission assembly includes a planet carrier and planet gears. The planet carrier is sleeved on the central shaft and fixedly connected to the central shaft. The planet gears are rotatably connected to the planet carrier. The torque adjustment assembly includes a first face gear and a second face gear, which are sleeved on the central shaft and rotatably connected to the central shaft. The tooth surfaces of the first face gear and the second face gear are arranged opposite to each other. The planetary carrier is located between the first face gear and the second face gear, and the planetary gears are meshed with the first face gear and the second face gear respectively. The axes of the first face gear and the second face gear intersect the axis of the planetary gear in the vertical direction. The drive assembly includes a first drive unit and a second drive unit. The output end of the first drive unit is fixedly connected to one end of the central shaft, and the output end of the second drive unit is fixedly connected to the first face gear or the second face gear, for driving the first face gear and the second face gear to rotate in opposite directions.

[0008] Optionally, the planet carrier has a through-hole along the axial direction of the central axis. The through-hole is located outside the shaft hole of the planet carrier and there are multiple through-holes distributed along the circumference of the planet carrier. Each of the mounting holes is fixed with a planetary shaft, and the planetary gears are fitted onto the planetary shafts one by one, with the planetary gears and the planetary shafts being rotatably connected by a first bearing.

[0009] Optionally, the planetary carrier includes a first frame and a second frame that are attached side by side along the axis of the planetary carrier. The opposing surfaces of the first frame and the second frame are respectively provided with corresponding limiting grooves. The limiting grooves cooperate with the arc-shaped outer wall of the planetary shaft, and the two opposing limiting grooves between the first frame and the second frame limit the planetary shaft in the direction perpendicular to its axis. A plurality of connecting pins are fixed on one of the opposing surfaces between the first frame and the second frame, and a first internal thread hole is formed on the connecting pin. A plurality of first screws are fixed on the other opposing surface between the first frame and the second frame, and the connecting pins are threadedly connected to the first screws one by one through the first internal thread hole. Internal splines are formed on the inner walls of the shaft holes of the first frame and the second frame, and external splines that mesh with the internal splines are formed on the outer wall of the central shaft.

[0010] Optionally, the assembly hole passes through the first frame and the second frame sequentially along the axial direction of the central axis, the limiting groove extends in the radial direction perpendicular to the axis of the planetary carrier and is distributed on both sides opposite to the assembly hole along its extension direction, the planetary shaft is placed in the assembly hole in the radial direction perpendicular to the axis of the planetary carrier, and the two limiting grooves corresponding between the first frame and the second frame respectively form radial limiting on both ends of the planetary shaft; The first bearing has an inner end face near the central shaft and a first spacer between it and the inner wall of the mounting hole. The first spacer is fitted onto the planetary shaft. The planetary shaft has a first convex ring formed on its outer wall inside the mounting hole. The first convex ring is located between the outer end face of the first bearing and the inner wall of the mounting hole, and it limits the planetary shaft in the axial direction.

[0011] Optionally, the torque adjustment assembly further includes bearing groups corresponding one-to-one with the first face gear and the second face gear; A second convex ring is formed on the inner wall of the shaft hole of both the first face gear and the second face gear. The bearing assembly includes second bearings distributed on both sides of the corresponding second convex ring and arranged opposite each other. The outer ring of the second bearing is connected to the inner wall of the shaft hole of the corresponding face gear, and the inner ring of the second bearing is connected to the outer wall of the central shaft. The two opposing second bearings in the bearing assembly form a pre-tightening structure that clamps the corresponding second convex ring. In the bearing assembly, a second spacer is provided between two opposing second bearings, and the second spacer is sleeved on the central shaft.

[0012] Optionally, the hydraulic vibratory hammer torque adjuster further includes locking nuts distributed on the outside of the two bearing assemblies, the central shaft has a threaded section formed on the outer wall of the shaft outside the bearing assembly, the locking nuts are sleeved on the central shaft, and the inner wall of the shaft hole of the locking nuts is threadedly connected to the threaded section; The second bearing in the bearing assembly, located on the inner side near the planetary carrier, is fitted with a third spacer. The third spacer is sleeved on the central shaft. The second bearing in the bearing assembly located on the outer side abuts against the locking nut, and the locking nut pre-tightens the bearing assembly in the axial direction by rotating its threads.

[0013] Optionally, a second internal threaded hole is provided on the outer side wall of the locking nut. The second internal threaded hole extends obliquely in a radial direction perpendicular to the axis of the locking nut and forms an opening on the inner wall of the shaft hole of the locking nut. A second screw is screwed into the second internal threaded hole, and the second screw contacts the outer wall of the central shaft through the thread to form a locking structure. The hydraulic vibratory hammer torque adjuster also includes end caps distributed on the outside of the two locking nuts, and a third bearing distributed on the outside of the two end caps. The end caps are sleeved on the central shaft, and a sealing ring is provided between the inner wall of the shaft hole of the end cap and the outer wall of the central shaft. The inner ring of the third bearing is connected to the outer wall of the central shaft, and the outer ring of the third bearing is used to connect with the housing shell of the vibratory hammer gearbox.

[0014] Optionally, the interior of the central shaft forms an oil supply channel extending along its axial direction, and the outer wall of the central shaft is provided with a plurality of oil outlet holes communicating with the oil supply channel. The distribution positions of the plurality of oil outlet holes correspond to the meshing points of the planetary gears and the face gears, and the rotational connection points of the face gears and the central shaft. The oil delivery channel has a connection interface formed on the end face of the central axis away from the first drive unit. A rotary joint is connected to the connection interface, and the rotary joint is connected to the oil supply pipeline of an external oil supply device.

[0015] Optionally, the torque adjustment assembly further includes a first cylindrical gear and a second cylindrical gear, wherein the first face gear is fitted and nested in the shaft hole of the first cylindrical gear, and the outer wall of the first face gear is fixedly connected to the inner wall of the shaft hole of the first cylindrical gear; the second face gear is fitted and nested in the shaft hole of the second cylindrical gear, and the outer wall of the second face gear is fixedly connected to the inner wall of the shaft hole of the second cylindrical gear. The first cylindrical gear and the second cylindrical gear form a transmission structure that meshes one-to-one with two sets of eccentric gear sets in the vibratory hammer gearbox.

[0016] This invention also discloses a torque adjustment method using the aforementioned hydraulic vibratory hammer torque adjuster, the torque adjustment method comprising: Obtain the eccentric torque generated between the first face gear and the second face gear under different relative phase differences, and establish a phase-moment mapping relationship based on the eccentric torque corresponding to different relative phase differences; Obtain the target eccentric torque of the hydraulic vibratory hammer torque adjuster, and obtain the target phase difference corresponding to the target eccentric torque according to the phase-moment mapping relationship; A first control signal is output to the second drive unit to drive the differential relative rotation between the first face gear and the second face gear, and the relative phase difference between the first face gear and the second face gear is acquired in real time. The vibration-damping phase difference when the eccentric torque is zero is extracted from the phase-moment mapping relationship. When the relative phase difference obtained in real time reaches the vibration-damping phase difference, the second drive unit stops and outputs a second control signal to the first drive unit to drive the central shaft to rotate faster. The rotational speed of the central shaft is acquired in real time. When the rotational speed at which the central shaft drives the transmission assembly and the torque adjustment assembly to rotate synchronously reaches the preset working speed, the first drive unit maintains the current rotational speed and outputs a third control signal to the second drive unit to continue driving the differential relative rotation between the first face gear and the second face gear until the relative phase difference acquired in real time gradually changes from the vibration damping phase difference to the target phase difference.

[0017] Compared with the prior art, the beneficial effects of the hydraulic vibratory hammer torque adjuster and torque adjustment method based on face gear transmission provided by the embodiments of the present invention are as follows: By utilizing the insensitivity of face gear transmission to axial installation errors, the meshing overlap between the first and second face gears and the planetary gears remains stable under vibration conditions, preventing increased tooth surface contact stress and solving the tooth surface failure problem caused by decreased meshing overlap in bevel gear differential schemes. The second drive unit can adjust the relative phase difference between the two face gears before the central shaft starts, ensuring that the eccentric torques of the two sets of eccentric gears cancel each other out, thus eliminating excitation force during torque adjustment and preventing starting resonance. After the central shaft reaches its operating speed, the second drive unit continues to change the relative phase difference, gradually increasing the combined eccentric torque of the two sets of eccentric gears from zero, achieving real-time stepless adjustment of the eccentric torque during operation. Attached Figure Description

[0018] The technical solution of the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. In the accompanying drawings: Figure 1 This is a schematic diagram of the overall structure of the hydraulic vibratory hammer torque adjuster provided in an embodiment of the present invention; Figure 2 This is a schematic diagram of the distribution of the first screw on the planetary carrier provided in an embodiment of the present invention; Figure 3 A schematic diagram of the internal structure of the hydraulic vibratory hammer torque adjuster provided in an embodiment of the present invention; Figure 4 This is a schematic diagram of the assembly of the planetary shaft and planetary gears provided in an embodiment of the present invention; Figure 5 This is a schematic diagram of the assembly of a face gear and a corresponding cylindrical gear provided in an embodiment of the present invention.

[0019] The markings in the attached diagram are as follows: 1. Central shaft; 11. Oil supply channel; 12. Oil outlet; 13. Rotary joint; 2. Planetary carrier; 21. Planetary gear; 22. Assembly hole; 23. Planetary shaft; 24. First frame; 25. Second frame; 26. Limiting groove; 27. Connecting pin; 28. First screw; 3. First face gear; 31. First cylindrical gear; 4. Second face gear; 41. Second cylindrical gear; 5. First bearing; 51. First spacer; 52. First convex ring; 6. Second convex ring; 7. Second bearing; 71. Second spacer; 72. Third spacer; 8. Locking nut; 81. Second internal threaded hole; 9. End cap. Detailed Implementation

[0020] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The preferred embodiments of the present invention will now be described in detail with reference to the accompanying drawings.

[0021] This invention discloses a hydraulic vibratory hammer torque adjuster based on face gear transmission, such as... Figure 1 As shown, it includes: Central axis 1; The transmission assembly includes a planet carrier 2 and planet gears 21. The planet carrier 2 is mounted on the central shaft 1 and is fixedly connected to the central shaft 1. The planet gears 21 are rotatably connected to the planet carrier 2. The torque adjustment assembly includes a first face gear 3 and a second face gear 4, which are sleeved on the central shaft 1 and rotatably connected to the central shaft 1. The tooth surfaces of the first face gear 3 and the second face gear are arranged opposite to each other. The planet carrier 2 is located between the first face gear 3 and the second face gear, and the planet gear 21 is meshed with the first face gear 3 and the second face gear respectively. The axes of the first face gear 3 and the second face gear intersect the axis of the planet gear 21 in the vertical direction. The drive assembly includes a first drive unit and a second drive unit. The output end of the first drive unit is fixedly connected to one end of the central shaft 1, and the output end of the second drive unit is fixedly connected to either the first face gear 3 or the second face gear 4, for driving the first face gear 3 and the second face gear 4 to rotate in opposite directions.

[0022] By implementing the above-described hydraulic vibratory hammer torque adjuster embodiment, firstly, by utilizing the insensitivity of cylindrical gears in face gear transmission to axial installation errors, the meshing overlap between the first face gear 3 and the second face gear 4 and the planetary gear 21 remains stable under vibration conditions. This avoids the increase in tooth surface contact stress due to axial movement, thereby solving the problems of pitting and scuffing failure caused by decreased meshing overlap in traditional bevel gear differential schemes. The tooth surface hardness of the face gear is 58-64 HRC, and the accuracy grade reaches level 7 of GB / T 10095.1-2008. The tooth surface is modified through tooth profile and tooth direction modification to reduce meshing noise and dynamic load, further improving the fatigue resistance of the tooth surface.

[0023] When the first drive unit drives the central shaft 1 to rotate, the central shaft 1 drives the planet carrier 2 and planet gears 21 to revolve around the central shaft 1. Since the first face gear 3 and the second face gear 4 share the same central shaft 1 and intersect the axis of the planet gears 21 perpendicularly, when the planet gears 21 revolve around the central shaft 1, their meshing points with the first face gear 3 and with the second face gear 4 are located at opposite ends of the planet gear 21's axial direction. The linear velocity directions of the planet gears 21 at these two meshing points are the same. Therefore, during their revolution, the planet gears 21 simultaneously drive the first face gear 3 and the second face gear 4 to rotate around the central shaft 1 in the same direction, without causing relative rotation of the two face gears without external additional drive. In other words, at this time, the first drive unit drives the rotation of the entire hydraulic vibratory hammer torque adjuster.

[0024] When the second drive unit independently drives the first face gear 3 or the second face gear 4 to rotate, the additional rotation of the face gear relative to the central shaft 1 is transmitted to the other face gear through the planetary gear 21, causing the other face gear to generate additional rotation in the opposite direction, thereby forming a relative phase difference between the first face gear 3 and the second face gear 4. This relative phase difference is transmitted to the two sets of eccentric gear sets, so that a corresponding phase difference is formed between the two sets of eccentric gear sets.

[0025] Therefore, before the central shaft 1 rotates, the second drive unit can adjust the relative phase difference to the point where the eccentric torques of the two sets of eccentric wheels cancel each other out, so that the torque adjuster does not generate excitation force during acceleration, eliminating the resonance phenomenon when the excitation frequency of the vibratory hammer crosses the natural frequency of the crane system during startup, and avoiding equipment damage caused by excessive crane amplitude.

[0026] Subsequently, the first drive unit drives the central shaft 1 to accelerate rotation. After the central shaft 1 reaches the working speed, the second drive unit continues to drive the first face gear 3 or the second face gear 4 to rotate, gradually changing the relative phase difference between the two face gears. This phase difference change is transmitted to the two sets of eccentric wheel sets, so that the combined eccentric torque of the two sets of eccentric wheel sets gradually increases from zero to the target value, thereby realizing the real-time stepless adjustment of the eccentric torque during operation. The excitation force amplitude can be adjusted according to changes in geological conditions without stopping the machine.

[0027] In the above-described embodiments, in soft soil layers, the eccentric moments of the two sets of eccentric wheel sets can be kept mutually canceling or only a small eccentric moment can be retained to prevent the pile from sinking too quickly and causing misalignment. In hard soil or rock layers, the combined eccentric moment of the two sets of eccentric wheel sets can be increased to overcome the pile driving resistance. The coordinated work of the first drive unit and the second drive unit enables the torque adjuster to be driven by the first drive unit alone to rotate and accelerate to the working speed during the start-up phase. During the acceleration process, the second drive unit maintains the vibration-damping phase difference to ensure that no excitation force is generated. After the working speed is reached, the second drive unit begins to adjust the phase to generate eccentric moment, thus separating the start-up process and the torque adjustment process in terms of timing. Preferably, both the first drive unit and the second drive unit are hydraulic motors, and the two hydraulic motors are controlled independently.

[0028] Furthermore, combined Figure 2 and Figure 3 As shown, the planet carrier 2 has an assembly hole 22 through the planet carrier 2 along the axial direction of the central axis 1. The assembly hole 22 is located outside the shaft hole of the planet carrier 2, and there are multiple assembly holes distributed along the circumference of the planet carrier 2. Each mounting hole 22 is fixed with a planetary shaft 23, and planetary gears 21 are fitted onto the planetary shaft 23 in a corresponding manner. The planetary gears 21 and the planetary shaft 23 are rotatably connected by the first bearing 5.

[0029] By implementing the above-described embodiment of the hydraulic vibratory hammer torque adjuster, multiple mounting holes 22 are distributed along the circumferential direction of the planetary carrier 2, so that multiple planetary shafts 23 can be evenly distributed on the planetary carrier 2 with the axis of the central shaft 1 as a reference. This ensures that multiple planetary gears 21 engage with the first face gear 3 and the second face gear 4 simultaneously, avoiding the impact load caused by the phase deviation of the planetary gears 21, where a single planetary gear 21 contacts first and the other planetary gears 21 contact later.

[0030] Secondly, by arranging multiple planetary gears 21, the meshing points of the planetary gears 21 with the first face gear 3 and the second face gear 4 are evenly distributed along the circumference. Multiple meshing points bear the load simultaneously to achieve power distribution. The torque transmitted by a single planetary gear 21 is reduced. The meshing load on the first face gear 3 and the second face gear 4 is evenly distributed along the circumference, which can effectively avoid the load being concentrated on a local tooth surface, reduce the force per unit tooth width, thereby reducing the tooth surface contact stress and delaying the occurrence of tooth surface pitting and scuffing failure.

[0031] Planetary gear 21 and planetary shaft 23 are rotatably connected by a first bearing 5, decoupling the rotational motion of planetary gear 21 from the revolution of planet carrier 2. The rotational speed and revolution speed of planetary gear 21 are independent, ensuring that planetary gear 21 can automatically match its rotational speed according to the rotational speeds of the first gear 3 and the second gear 4, avoiding tooth surface slippage and increased wear caused by mismatch between rotational and revolution speeds. Preferably, the planetary gears are spur gears with a clearance fit to the planetary gear 21 shaft.

[0032] Furthermore, combined Figures 1-4 As shown, the planetary carrier 2 includes a first frame 24 and a second frame 25 that are attached side by side along the axis of the planetary carrier 2. The opposing surfaces of the first frame 24 and the second frame 25 are respectively provided with corresponding limiting grooves 26. The limiting grooves 26 cooperate with the arc-shaped outer wall of the planetary shaft 23, and the two opposing limiting grooves 26 between the first frame 24 and the second frame 25 limit the planetary shaft 23 in the direction perpendicular to its axis. A plurality of connecting pins 27 are fixed on one of the opposing surfaces between the first frame 24 and the second frame 25. A first internal thread hole is formed on the connecting pin 27. A plurality of first screws 28 are fixed on the other opposing surface between the first frame 24 and the second frame 25. The connecting pins 27 are threadedly connected to the first screws 28 one by one through the first internal thread hole. Internal splines are formed on the inner walls of the shaft holes of the first frame 24 and the second frame 25, respectively, and external splines that mesh with the internal splines are formed on the outer wall of the central shaft 1.

[0033] By implementing the above-described embodiment of the hydraulic vibratory hammer torque adjuster, the first frame 24 and the second frame 25 are detachably connected, and the corresponding limiting grooves 26 between the first frame 24 and the second frame 25 are used to ensure that when assembling the planetary shaft 23, it is first placed in the limiting groove 26 of the first frame 24, and then the second frame 25 is closed and fixed. There is no need to use a press-fitting method to install the planetary shaft 23 into the shaft hole, thus avoiding damage to the planetary shaft 23 and the planet carrier 2 during the press-fitting process.

[0034] After the first frame 24 and the second frame 25 are connected, the two opposing limiting grooves 26 limit the planetary shaft 23 in the direction perpendicular to its axis, so that the planetary shaft 23 is fixed in the plane perpendicular to its own axis by the limiting grooves 26. No additional fasteners are needed to radially fix the planetary shaft 23, avoiding radial movement of the planetary shaft 23 due to loosening of fasteners under vibration conditions, and ensuring that the meshing center distance between the planetary gear 21 and the first face gear 3 and the second face gear 4 remains stable in the vibration environment.

[0035] In addition, by using the connecting pin 27 and the first screw 28 to connect in a corresponding threaded manner, the first frame 24 and the second frame 25 can be detachably fixed through the threaded connection. The threaded connection can provide a stable preload force, so that the first frame 24 and the second frame 25 always remain in close contact under vibration conditions, and avoid the failure of the radial limit of the limiting groove 26 on the planetary shaft 23 due to the separation of the frame.

[0036] The first carrier 24 and the second carrier 25 are connected by internal splines and external splines on the central shaft 1, enabling torque transmission between the central shaft 1 and the planet carrier 2. This spline connection allows the planet carrier 2 to be adjusted along the axial direction of the central shaft 1. During assembly, the axial position of the planet carrier 2 on the central shaft 1 can be adjusted to compensate for machining and assembly errors, ensuring correct alignment of the meshing positions of the multiple planetary gears 21 with the first face gear 3 and the second face gear 4. This avoids misalignment between the tooth width of the planetary gears 21 and the face gears due to axial position deviation of the planet carrier 2. Preferably, the first carrier 24 and the second carrier 25 are symmetrically arranged disc-shaped structures, connected as one unit by connecting pins 27 and first screws 28 to form a rigid planet carrier 2.

[0037] Furthermore, the assembly hole 22 passes through the first frame 24 and the second frame 25 sequentially along the axial direction of the central axis 1. The limiting groove 26 extends in the radial direction perpendicular to the axis of the planetary carrier 2 and is distributed on opposite sides of the assembly hole 22 along its extension direction. The planetary shaft 23 is placed in the assembly hole 22 in the radial direction perpendicular to the axis of the planetary carrier 2, and the two limiting grooves 26 corresponding between the first frame 24 and the second frame 25 respectively form radial limits on the two ends of the planetary shaft 23. The first bearing 5 is located near the inner end face of the central shaft 1, and a first spacer 51 is provided between it and the inner wall of the mounting hole 22. The first spacer 51 is sleeved on the planetary shaft 23. The planetary shaft 23 is located on the outer wall of the shaft inside the mounting hole 22, and a first protruding ring 52 is formed. The first protruding ring 52 is located between the outer end face of the first bearing 5 and the inner wall of the mounting hole 22, and limits the planetary shaft 23 in the axial direction.

[0038] By implementing the above-described embodiment of the hydraulic vibratory hammer torque adjuster, the assembly hole 22 passes through the first frame 24 and the second frame 25 sequentially along the axial direction of the central shaft 1, so that the planetary shaft 23 can be inserted into the assembly hole 22 from the radial direction of the planetary carrier 2 via the limiting groove 26, thereby reducing the assembly difficulty.

[0039] The two corresponding limiting grooves 26 between the first carrier 24 and the second carrier 25 form radial limits on both ends of the planetary shaft 23, constraining the planetary shaft 23 in a plane perpendicular to its own axis and preventing radial displacement. Simultaneously, the middle part of the planetary shaft 23, located within the mounting hole 22, is used to install the first bearing 5 and the first spacer 51. This axially separates the end positioning function and the middle bearing function of the planetary shaft 23, ensuring that the radial limiting at the ends does not interfere with the fit between the middle part and the first bearing 5 and the first spacer 51. The limiting grooves 26 extend radially to the outer ring wall of the planetary carrier 2, forming a through-structure from the inner ring to the outer ring on the end face of the planetary carrier 2. The mounting hole 22 maintains a complete axial through-structure within the planetary carrier 2, and the main bearing area of ​​the mounting hole 22 is not weakened by the limiting grooves 26, ensuring that the hole wall of the mounting hole 22 has sufficient contact area to withstand the radial load generated by the meshing of the planetary gears 21.

[0040] The first spacer 51 is fitted onto the planetary shaft 23, and the axial position of the first bearing 5 on the planetary shaft 23 can be adjusted by selecting first spacers 51 of different thicknesses. At the same time, the first convex ring 52 and the first spacer 51 respectively form a bidirectional clamping and positioning of the first bearing 5 from two axial directions. The diameter of the first convex ring 52 is configured to be larger than the diameter of the two relative limiting grooves 26 after they are joined together, so as to limit the planetary shaft 23 in the axial direction and prevent the planetary shaft 23 from moving along its own axial direction under vibration conditions, thus constraining the planetary shaft 23 in the axial direction.

[0041] The axial constraint formed by the first convex ring 52 on the planetary axis 23, together with the radial constraint formed by the limiting groove 26 on the planetary axis 23, constitutes all the degrees of freedom constraints of the planetary axis 23 in space except for rotation around its own axis, ensuring that the planetary gear 21 can only rotate around the planetary axis 23 and cannot generate movement in other directions.

[0042] Furthermore, looking back Figure 3 The torque adjustment assembly also includes bearing groups that correspond one-to-one with the first face gear 3 and the second face gear 4; A second convex ring 6 is formed on the inner wall of the shaft hole of the first gear 3 and the second gear 4. The bearing assembly includes a second bearing 7 distributed on both sides of the corresponding second convex ring 6 and arranged opposite to each other. The outer ring of the second bearing 7 is connected to the inner wall of the shaft hole of the corresponding gear, and the inner ring of the second bearing 7 is connected to the outer wall of the central shaft 1. The two opposing second bearings 7 in the bearing assembly form a pre-tightening structure that clamps the corresponding second convex ring 6. Among them, a second spacer 71 is provided between two opposing second bearings 7 in the bearing assembly, and the second spacer 71 is sleeved on the central shaft 1.

[0043] By implementing the above-described hydraulic vibratory hammer torque adjuster embodiment, the bearing assembly allows the first face gear 3 and the second face gear 4 to be supported on the central shaft 1 by their respective two second bearings 7, thereby achieving a rotational connection between the face gears and the central shaft 1. At the same time, the two second bearings 7 jointly bear the radial load generated by the face gears during rotation.

[0044] Furthermore, the two opposing second bearings 7 in the bearing assembly form a preload structure that clamps the corresponding second convex ring 6, so that the axial positions of the first face gear 3 and the second face gear 4 on the central shaft 1 are simultaneously constrained from two directions by the second bearings 7 on both sides. When the face gears are subjected to alternating axial forces in both directions under vibration conditions, this clamping structure can provide limits in both directions, preventing the face gears from moving bidirectionally along the axis of the central shaft 1, and ensuring the stability of the relative positions of the first face gear 3 and the second face gear 4 with the planetary gear 21 in the axial direction.

[0045] The second spacer 71 is fitted onto the central shaft 1, axially separating the two opposing second bearings 7 in the bearing assembly. The axial distance between the inner rings of the two second bearings 7 is determined by the thickness of the second spacer 71, thereby controlling the clamping degree of the two second bearings 7 onto the second convex ring 6. This prevents excessive preload leading to excessive bearing temperature rise or insufficient preload leading to increased bearing clearance. The preload of the clamping preload structure can be precisely set during assembly by selecting second spacers 71 of different thicknesses, eliminating the need for additional preload adjustment after assembly. Preferably, the second bearings 7 are tapered roller bearings used in pairs, mounted on both sides of the face gear, bearing radial loads and bidirectional axial loads.

[0046] Furthermore, combined Figure 1 and Figure 3 As shown, the hydraulic vibratory hammer torque adjuster also includes locking nuts 8 distributed on the outside of the two bearing groups. The central shaft 1 has a threaded section formed on the outer wall of the shaft outside the bearing group. The locking nuts 8 are sleeved on the central shaft 1, and the inner wall of the shaft hole of the locking nuts 8 is threadedly connected to the threaded section. The inner second bearing 7 in the bearing assembly, which is close to the planet carrier 2, is fitted with a third spacer 72. The third spacer 72 is sleeved on the central shaft 1. The outer second bearing 7 in the bearing assembly abuts against the locking nut 8, and the locking nut 8 forms a preload on the bearing assembly in the axial direction by rotating the thread.

[0047] By implementing the above-described embodiment of the hydraulic vibratory hammer torque adjuster, the locking nuts 8 are distributed on the outer sides of the two bearing assemblies. By rotating the locking nuts 8, they are pressed inward along the axial direction of the central shaft 1 to the outer second bearing 7 in the bearing assembly. The axial preload is transmitted through the outer second bearing 7 to the second convex ring 6, and then through the second convex ring 6 to the inner second bearing 7, thus forming an axial preload on the entire bearing assembly. This locks the clamping relationship between the two second bearings 7 and the second convex ring 6 under the action of the preload, preventing the bearing assembly from axially loosening due to the attenuation of the clamping force under vibration conditions.

[0048] The third spacer 72 is fitted onto the central shaft 1. When the locking nut 8 applies preload, the inner second bearing 7 abuts against the end face of the planetary carrier 2 through the third spacer 72, allowing the preload to be transmitted to the planetary carrier 2 via the third spacer 72, whereby the planetary carrier 2 bears the axial reaction force. Simultaneously, the third spacer 72 separates the inner second bearing 7 from the end face of the planetary carrier 2, preventing direct contact and friction between the inner second bearing 7 and the end face of the planetary carrier 2. Therefore, the entire bearing assembly is axially clamped between the locking nut 8 and the planetary carrier 2, forming a closed preload cycle. This ensures that the preload of the bearing assembly does not depend on an external pressure device; under vibration conditions, maintaining the self-locking characteristic of the threaded connection between the locking nut 8 and the threaded section is sufficient to maintain a constant preload.

[0049] As described above, the axial distance between the bearing assembly and the planetary carrier 2 can be adjusted by selecting third spacers 72 of different thicknesses, so that the symmetry of the first face gear 3 and the second face gear 4 relative to the planetary gear 21 can be precisely set by selecting the thickness of the third spacer 72. Preferably, the locking nut 8 is provided with a washer to prevent the locking nut 8 from loosening under vibration conditions.

[0050] Furthermore, a second internal threaded hole 81 is provided on the outer wall of the locking nut 8. The second internal threaded hole 81 extends obliquely in the radial direction perpendicular to the axis of the locking nut 8 and forms an opening on the inner wall of the shaft hole of the locking nut 8. A second screw is screwed into the second internal threaded hole 81, and the second screw contacts the outer wall of the central shaft 1 through the thread to form a locking structure. The hydraulic vibratory hammer torque adjuster also includes end caps 9 distributed on the outside of the two locking nuts 8, and a third bearing distributed on the outside of the two end caps 9. The end caps 9 are sleeved on the central shaft 1, and a sealing ring is provided between the inner wall of the shaft hole of the end cap 9 and the outer wall of the central shaft 1. The inner ring of the third bearing is connected to the outer wall of the central shaft 1, and the outer ring of the third bearing is used to connect with the housing shell of the vibratory hammer gearbox.

[0051] By implementing the above-described embodiment of the hydraulic vibratory hammer torque adjuster, based on the axial preload provided by the locking nut 8 through the threaded connection, the second screw is screwed into the outer wall of the locking nut 8 in the radial direction and pressed against the central shaft 1. This creates additional frictional locking between the locking nut 8 and the central shaft 1 through the radial pressing action of the second screw. This prevents the locking nut 8 from loosening along the threaded section due to inertial torque or alternating load under vibration conditions, ensuring that the preload of the bearing assembly does not decrease under vibration conditions and maintaining the clamping preload state between the two second bearings 7 and the second convex ring 6.

[0052] End caps 9 are distributed outside the two locking nuts 8 and sleeved on the central shaft 1, encapsulating the locking nuts 8 within the space between the end caps 9 and the bearing assembly. This keeps the locking nuts 8 in a closed cavity, isolating them from external dust and moisture, and preventing external contaminants from entering the threaded connection area, which could cause jamming or wear of the threaded pair due to foreign matter. A sealing ring forms a circumferential seal between the end caps 9 and the central shaft 1, isolating the space containing the bearing assembly from the external environment. This allows the lubricating oil to remain within the closed space of the bearing assembly, while preventing external mud, dust, and moisture from invading back into the bearing assembly.

[0053] The third bearing allows the central shaft 1, planetary carrier 2, locking nut 8, and end cover 9, which are fixed to the central shaft 1, to be supported as a whole within the vibratory hammer gearbox. While allowing the central shaft 1 to rotate freely relative to the vibratory hammer gearbox, the third bearing transmits the radial and axial loads generated by the eccentric mass during the rotation of the central shaft 1 to the outer shell of the vibratory hammer gearbox. This prevents the load from acting directly on the meshing position of the first face gear 3 and the second face gear 4 with the planetary gear 21, and prevents the meshing tooth surfaces from generating additional contact stress due to excessive external loads. At the same time, it prevents the load from being directly transmitted to the second bearing 7 between the first face gear 3 and the second face gear 4 and the central shaft 1, which would cause the bearing to overload.

[0054] As described above, the inclined second internal threaded hole 81 creates an angle between the axis of the second screw and the axis of the central shaft 1, rather than a perpendicular intersection. When the second screw is screwed in, its end abuts against the surface of the central shaft 1 along the inclined direction. Compared to a radial perpendicular abutment method, this generates a larger normal contact force component on the surface of the central shaft 1, improving the anti-loosening ability between the locking nut 8 and the central shaft 1. Preferably, the second screw is a hexagonal socket head cap screw to prevent the locking nut 8 from loosening.

[0055] Furthermore, looking back Figure 3 The interior of the central shaft 1 has an oil supply channel 11 extending along its axial direction. The outer wall of the central shaft 1 has several oil outlet holes 12 that communicate with the oil supply channel 11. The distribution of the oil outlet holes 12 corresponds to the meshing points of the planetary gear 21 and each face gear, and the rotational connection points of each face gear and the central shaft 1. An interface is formed on the end face of the central shaft 1 away from the first drive unit in the oil supply channel 11. A rotary joint 13 is connected to the interface, and the rotary joint 13 is connected to the oil supply pipeline of an external oil supply device.

[0056] By implementing the above-described embodiment of the hydraulic vibratory hammer torque adjuster, the rotary joint 13 allows lubricating oil in the oil supply line to enter the oil delivery channel 11, which rotates with the central shaft 1, through the rotary joint 13 while the central shaft 1 is continuously rotating. As a dynamic sealing connection element between the stationary pipeline and the rotating component, the rotary joint 13 enables a continuous supply of lubricating oil from the stationary oil supply line to the rotating central shaft 1, preventing the oil supply line from twisting or tangling due to the rotation of the central shaft 1.

[0057] The distribution of several oil outlet holes 12 corresponds to the meshing points of the planetary gears 21 and each faceted gear, and the rotational connection points of each faceted gear and the central shaft 1. This allows the lubricating oil in the oil delivery channel 11, under centrifugal force, to be directly thrown from the oil delivery channel 11, which rotates with the central shaft 1, through the oil outlet holes 12 to the meshing points of the planetary gears 21 and the first faceted gear 3, the planetary gears 21 and the second faceted gear 4, and the rotational connection points of the first faceted gear 3 and the second faceted gear 4 with the central shaft 1. Under centrifugal force, the lubricating oil gains additional kinetic energy, is thrown radially, and covers the tooth contact area and the bearing raceway surface, achieving direct lubrication of each meshing point and rotational connection point.

[0058] The aforementioned lubrication circuit is fully integrated within the central shaft 1, eliminating the need for external lubrication pipes on the torque adjuster. This avoids the risk of oil leakage caused by loose or broken pipe joints under vibration conditions, which is common with external piping. Furthermore, the lubricating oil flows directly from inside the central shaft 1 through the oil outlet 12 to each lubrication point, shortening the flow path from the oil inlet to each lubrication point and reducing pressure loss during flow. Preferably, the torque adjuster employs a closed-loop self-lubricating system with oil bath lubrication for the planetary gears and face gears. Lubricating oil is supplied through channels within the shaft, passes through the bearings, and then returns to the oil sump, forming a circulating lubrication system.

[0059] Furthermore, combined Figure 1 and Figure 5 As shown, the torque adjustment assembly also includes a first cylindrical gear 31 and a second cylindrical gear 41. The first face gear 3 is fitted and nested in the shaft hole of the first cylindrical gear 31, and the outer wall of the first face gear 3 is fixedly connected to the inner wall of the shaft hole of the first cylindrical gear 31. The second face gear 4 is fitted and nested in the shaft hole of the second cylindrical gear 41, and the outer wall of the second face gear 4 is fixedly connected to the inner wall of the shaft hole of the second cylindrical gear 41. The first cylindrical gear 31 and the second cylindrical gear 41 form a transmission structure that meshes one-to-one with two sets of eccentric gear sets in the vibratory hammer gearbox.

[0060] By implementing the above-described embodiment of the hydraulic vibratory hammer torque adjuster, the first face gear 3 and the first cylindrical gear 31 are nested together, and the second face gear 4 and the second cylindrical gear 41 are nested together. The face gear and the corresponding cylindrical gear share a common mounting position in the radial direction, eliminating the need for separate shafts and bearings for the cylindrical gears. This avoids adding extra gear shafts to the vibratory hammer gearbox, which would complicate the gearbox structure and increase the axial dimensions. Simultaneously, the power transmission between the face gear and the cylindrical gear does not require a separate intermediate drive shaft. The rotation of the face gear is directly transmitted to the cylindrical gear, and the rotation of the cylindrical gear is directly transmitted to the eccentric wheel set meshing with it. This shortens the transmission chain between the face gear and the eccentric wheel set to a single-stage meshing transmission of face gear-cylindrical gear-eccentric wheel set.

[0061] When the second drive unit drives the first face gear 3 or the second face gear 4 to rotate independently, the phase change of the face gear relative to the other face gear is directly transmitted to the eccentric wheel set meshing with the cylindrical gear fixed to the face gear. This causes the phase difference between the two eccentric wheel sets to change synchronously with the relative phase difference between the two face gears. The transmission ratio between the face gear and the eccentric wheel set is determined by the tooth ratio between the cylindrical gear and the gear on the eccentric wheel set. By pre-setting the tooth ratio between the cylindrical gear and the gear on the eccentric wheel set, the phase transmission accuracy meets the design requirements.

[0062] This invention also discloses a torque adjustment method, which uses the above-mentioned hydraulic vibratory hammer torque adjuster. The torque adjustment method includes: Obtain the eccentric torque generated between the first gear 3 and the second gear 4 under different relative phase differences, and establish a phase-moment mapping relationship based on the eccentric torque corresponding to different relative phase differences; Obtain the target eccentric torque of the hydraulic vibratory hammer torque adjuster, and obtain the target phase difference corresponding to the target eccentric torque according to the phase-moment mapping relationship; The first control signal is output to the second drive unit to drive the differential relative rotation between the first face gear 3 and the second face gear 4, and the relative phase difference between the first face gear 3 and the second face gear 4 is obtained in real time. The vibration-damping phase difference when the eccentric torque is zero is extracted from the phase-moment mapping relationship. When the relative phase difference obtained in real time reaches the vibration-damping phase difference, the second drive unit stops and outputs a second control signal to the first drive unit to drive the central shaft 1 to accelerate rotation. The rotational speed of the central shaft 1 is acquired in real time. When the rotational speed of the central shaft 1 driving the transmission component and the torque adjustment component to rotate synchronously reaches the preset working speed, the first drive unit maintains the current speed and outputs a third control signal to the second drive unit to continue driving the differential relative rotation between the first face gear 3 and the second face gear 4 until the relative phase difference acquired in real time gradually changes from the vibration damping phase difference to the target phase difference.

[0063] By implementing the above-described torque adjustment method, firstly, a phase-moment mapping relationship is established, solidifying the correspondence between eccentric torque and relative phase difference in a mapped form. This provides a basis for querying the target phase difference in subsequent adjustment processes, eliminating the need to recalculate the correspondence between eccentric torque and phase difference during each adjustment, thus improving the adjustment response speed. Secondly, the target phase difference corresponding to the target eccentric torque is obtained based on the phase-moment mapping relationship, directly converting the target eccentric torque into an executable target phase difference. This avoids the accumulation of deviations between the target eccentric torque and the actual output eccentric torque caused by nonlinearity in the transmission system.

[0064] The output of the first control signal drives the differential relative rotation between the first face gear 3 and the second face gear 4. By acquiring the relative phase difference in real time, a closed-loop feedback is formed for the adjustment process, enabling the actual phase difference during the adjustment process to determine whether the target position has been reached. When the real-time acquired relative phase difference reaches the vibration-damping phase difference, the second drive unit stops, so that the torque adjuster is pre-positioned in a vibration-damping state with zero eccentric torque before startup, providing a phase reference for vibration-free startup in this state.

[0065] The torque adjustment stage is only entered after the central shaft 1 reaches the preset operating speed. That is, when the central shaft 1 drives the transmission assembly and torque adjustment assembly to rotate synchronously at the preset operating speed, the first drive unit maintains the current speed, ensuring stable operation of the central shaft 1 at the operating speed. This prevents additional dynamic loads from occurring at the meshing point of the face gear and planetary gear 21 due to speed fluctuations in the central shaft 1 during torque adjustment. A third control signal is output to continue driving the differential relative rotation between the first face gear 3 and the second face gear 4, causing the combined eccentric torque generated by the two sets of eccentric gears to gradually increase from zero to the target eccentric torque, achieving a smooth transition of the eccentric torque from the starting state to the operating state.

[0066] It should be understood that the above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit them. Those skilled in the art can modify the technical solutions described in the above embodiments, or make equivalent substitutions for some of the technical features; and all such modifications and substitutions should fall within the protection scope of the appended claims of the present invention.

Claims

1. A torque adjuster for a hydraulic vibratory hammer based on face gear transmission, characterized in that: The hydraulic vibratory hammer torque adjuster includes: Central axis; The transmission assembly includes a planet carrier and planet gears. The planet carrier is sleeved on the central shaft and fixedly connected to the central shaft. The planet gears are rotatably connected to the planet carrier. The torque adjustment assembly includes a first face gear and a second face gear, which are sleeved on the central shaft and rotatably connected to the central shaft. The tooth surfaces of the first face gear and the second face gear are arranged opposite to each other. The planetary carrier is located between the first face gear and the second face gear, and the planetary gears are meshed with the first face gear and the second face gear respectively. The axes of the first face gear and the second face gear intersect the axis of the planetary gear in the vertical direction. The drive assembly includes a first drive unit and a second drive unit. The output end of the first drive unit is fixedly connected to one end of the central shaft, and the output end of the second drive unit is fixedly connected to the first face gear or the second face gear, for driving the first face gear and the second face gear to rotate in opposite directions.

2. The hydraulic vibratory hammer torque adjuster based on face gear transmission according to claim 1, characterized in that: The planet carrier has a through-hole along the axial direction of the central axis. The through-hole is located outside the shaft hole of the planet carrier and there are multiple through-holes distributed along the circumference of the planet carrier. Each of the mounting holes is fixed with a planetary shaft, and the planetary gears are fitted onto the planetary shafts one by one, with the planetary gears and the planetary shafts being rotatably connected by a first bearing.

3. The hydraulic vibratory hammer torque adjuster based on face gear transmission according to claim 2, characterized in that: The planetary carrier includes a first frame and a second frame that are attached side by side along the axis of the planetary carrier. The opposing surfaces of the first frame and the second frame are respectively provided with corresponding limiting grooves. The limiting grooves cooperate with the arc-shaped outer wall of the planetary shaft, and the two opposing limiting grooves between the first frame and the second frame limit the planetary shaft in the direction perpendicular to its axis. A plurality of connecting pins are fixed on one of the opposing surfaces between the first frame and the second frame, and a first internal thread hole is formed on the connecting pin. A plurality of first screws are fixed on the other opposing surface between the first frame and the second frame, and the connecting pins are threadedly connected to the first screws one by one through the first internal thread hole. Internal splines are formed on the inner walls of the shaft holes of the first frame and the second frame, and external splines that mesh with the internal splines are formed on the outer wall of the central shaft.

4. The hydraulic vibratory hammer torque adjuster based on face gear transmission according to claim 3, characterized in that: The assembly hole passes through the first frame and the second frame sequentially along the axial direction of the central axis. The limiting groove extends in the radial direction perpendicular to the axis of the planetary carrier and is distributed on both sides of the assembly hole along its extension direction. The planetary shaft is placed in the assembly hole in the radial direction perpendicular to the axis of the planetary carrier, and the two limiting grooves corresponding between the first frame and the second frame respectively form radial limiting on both ends of the planetary shaft. The first bearing has an inner end face near the central shaft and a first spacer between it and the inner wall of the mounting hole. The first spacer is fitted onto the planetary shaft. The planetary shaft has a first convex ring formed on its outer wall inside the mounting hole. The first convex ring is located between the outer end face of the first bearing and the inner wall of the mounting hole, and it limits the planetary shaft in the axial direction.

5. The hydraulic vibratory hammer torque adjuster based on face gear transmission according to claim 1, characterized in that: The torque adjustment assembly also includes bearing groups that correspond one-to-one with the first face gear and the second face gear; A second convex ring is formed on the inner wall of the shaft hole of both the first face gear and the second face gear. The bearing assembly includes second bearings distributed on both sides of the corresponding second convex ring and arranged opposite each other. The outer ring of the second bearing is connected to the inner wall of the shaft hole of the corresponding face gear, and the inner ring of the second bearing is connected to the outer wall of the central shaft. The two opposing second bearings in the bearing assembly form a pre-tightening structure that clamps the corresponding second convex ring. In the bearing assembly, a second spacer is provided between two opposing second bearings, and the second spacer is sleeved on the central shaft.

6. The hydraulic vibratory hammer torque adjuster based on face gear transmission according to claim 5, characterized in that: The hydraulic vibratory hammer torque adjuster also includes locking nuts distributed on the outside of the two bearing assemblies. The central shaft has a threaded section formed on the outer wall of the shaft outside the bearing assembly. The locking nuts are sleeved on the central shaft, and the inner wall of the shaft hole of the locking nuts is threadedly connected to the threaded section. The second bearing in the bearing assembly, located on the inner side near the planetary carrier, is fitted with a third spacer. The third spacer is sleeved on the central shaft. The second bearing in the bearing assembly located on the outer side abuts against the locking nut, and the locking nut pre-tightens the bearing assembly in the axial direction by rotating its threads.

7. The hydraulic vibratory hammer torque adjuster based on face gear transmission according to claim 6, characterized in that: The outer side wall of the locking nut is provided with a second internal thread hole. The second internal thread hole extends obliquely in a radial direction perpendicular to the axis of the locking nut and forms an opening on the inner wall of the shaft hole of the locking nut. A second screw is screwed into the second internal thread hole, and the second screw contacts the outer wall of the central shaft through the thread to form a locking structure. The hydraulic vibratory hammer torque adjuster also includes end caps distributed on the outside of the two locking nuts, and a third bearing distributed on the outside of the two end caps. The end caps are sleeved on the central shaft, and a sealing ring is provided between the inner wall of the shaft hole of the end cap and the outer wall of the central shaft. The inner ring of the third bearing is connected to the outer wall of the central shaft, and the outer ring of the third bearing is used to connect with the housing shell of the vibratory hammer gearbox.

8. The hydraulic vibratory hammer torque adjuster based on face gear transmission according to claim 1, characterized in that: The interior of the central shaft has an oil supply channel extending along its axial direction. The outer wall of the central shaft has several oil outlet holes that communicate with the oil supply channel. The distribution of the oil outlet holes corresponds to the meshing points of the planetary gears and the face gears, and the rotational connection points of the face gears and the central shaft. The oil delivery channel has a connection interface formed on the end face of the central axis away from the first drive unit. A rotary joint is connected to the connection interface, and the rotary joint is connected to the oil supply pipeline of an external oil supply device.

9. The hydraulic vibratory hammer torque adjuster based on face gear transmission according to claim 1, characterized in that: The torque adjustment assembly further includes a first cylindrical gear and a second cylindrical gear. The first face gear is fitted and nested in the shaft hole of the first cylindrical gear, and the outer wall of the first face gear is fixedly connected to the inner wall of the shaft hole of the first cylindrical gear. The second face gear is fitted and nested in the shaft hole of the second cylindrical gear, and the outer wall of the second face gear is fixedly connected to the inner wall of the shaft hole of the second cylindrical gear. The first cylindrical gear and the second cylindrical gear form a transmission structure that meshes one-to-one with two sets of eccentric gear sets in the vibratory hammer gearbox.

10. A torque adjustment method, employing the hydraulic vibratory hammer torque adjuster according to any one of claims 1-9, characterized in that, The torque adjustment method includes: Obtain the eccentric torque generated between the first face gear and the second face gear under different relative phase differences, and establish a phase-moment mapping relationship based on the eccentric torque corresponding to different relative phase differences; Obtain the target eccentric torque of the hydraulic vibratory hammer torque adjuster, and obtain the target phase difference corresponding to the target eccentric torque according to the phase-moment mapping relationship; A first control signal is output to the second drive unit to drive the differential relative rotation between the first face gear and the second face gear, and the relative phase difference between the first face gear and the second face gear is acquired in real time. The vibration-damping phase difference when the eccentric torque is zero is extracted from the phase-moment mapping relationship. When the relative phase difference obtained in real time reaches the vibration-damping phase difference, the second drive unit stops and outputs a second control signal to the first drive unit to drive the central shaft to rotate faster. The rotational speed of the central shaft is acquired in real time. When the rotational speed at which the central shaft drives the transmission assembly and the torque adjustment assembly to rotate synchronously reaches the preset working speed, the first drive unit maintains the current rotational speed and outputs a third control signal to the second drive unit to continue driving the differential relative rotation between the first face gear and the second face gear until the relative phase difference acquired in real time gradually changes from the vibration damping phase difference to the target phase difference.

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