High frequency hydraulic vibration rod

Abstract

The application discloses a high-frequency hydraulic vibration rod, characterized in that: comprising a vibrating shell assembly, a hydraulic power transmission assembly, a hydraulic pipeline protection assembly, and an eccentric excitation assembly; the hydraulic power transmission assembly and the eccentric excitation assembly are detachably assembled in the interior of the vibrating shell assembly; the hydraulic pipeline assembly is connected with the hydraulic power transmission assembly; the front sealing end cover comprises an inclined hole penetrating through the whole cover body and communicating with the central through hole; the eccentric excitation assembly is internally provided with an eccentric block, and the eccentric block comprises an eccentric main shaft and an eccentric block body integrally formed in the middle position of the eccentric main shaft. The inclined hole of the application is arranged in the fixed front sealing end cover, and the inclined hole is connected with the large-flow communication cross section pressure relief channel, the flow resistance is small, the pressure of the shaft end lubricating cavity is quickly released, the oil seal leakage is eliminated, the circulating lubricating oil channel is formed, the bearing and the oil seal are continuously cooled and lubricated, and the service life of the vulnerable parts is greatly prolonged.

Description

Technical Field

[0001] This invention relates to a vibrating rod, and more particularly to a high-frequency hydraulic vibrating rod. Background Technology

[0002] In the construction of existing cast-in-place concrete structures, the newly poured concrete is a loose mixture of aggregates, cement mortar, and air, containing a large number of gaps and closed air bubbles. If the air bubbles are not removed and the aggregates are not compacted through effective vibration, the concrete is prone to quality defects such as honeycomb, pitting, voids, looseness, and delamination after hardening. This directly reduces the compressive strength, impermeability, and overall durability of the concrete structure, and in severe cases, it can cause structural safety hazards. Therefore, the vibration process is a core and critical process in concrete construction.

[0003] Immersion concrete vibrators are the core equipment for cast-in-place concrete construction. Their working principle relies on the high-speed rotation of the internal eccentric rotating mechanism to generate periodic centrifugal excitation force, which causes the concrete mixture to vibrate at high frequency, eliminating air bubbles trapped inside the concrete and improving the density, strength and appearance quality of the concrete.

[0004] The gear-driven hydraulic motor inside the vibratory bar drives the eccentric block to generate tamping vibration. The meshing clearance of the gears will cause internal oil leakage. An oil leakage and pressure relief structure is required to lubricate and reduce pressure on the output end bearing and oil seal. The existing solution is to open an axial through hole inside the rotating output gear shaft as the only oil leakage channel. Although it can alleviate the oil leakage problem to a certain extent, it has many inherent defects under long-term high-speed heavy-load paving conditions. (1) The narrow flow channel of the long and thin shaft core has a large fluid resistance and cannot quickly discharge the lubricating oil in the cavity. It is easy to cause pressure buildup in the cavity. Continuous high pressure impact on the oil seal can easily cause shaft head leakage. Mud can easily enter the motor and cause damage to internal parts. At the same time, the deep hole of the shaft core is difficult to process, has a high scrap rate and high production cost. The oil passage needs to be precisely aligned during assembly. Even a slight deviation will block the pressure relief channel, resulting in a high defect rate in batch assembly. It can only passively discharge hot oil and cannot form a circulating lubrication and cooling oil circuit. The bearings and oil seals are prone to high-temperature aging and wear. Moreover, the oil passage has poor exhaust capacity. The gas accumulation in the cavity will form gas resistance, which will cause unstable motor speed and cavitation loss of parts. When the motor reverses direction, the oil discharge resistance of the straight hole increases sharply, and the oil leakage problem is further aggravated. Once the oil passage is blocked, the motor must be completely disassembled to clear it. On-site maintenance is cumbersome and causes serious work delays.

[0005] In addition, the eccentric excitation structure of vibrators on the market is mainly divided into two categories: The first type is the split structure: the optical shaft and the independent eccentric block are machined separately, and the eccentric block is fixed to the drive shaft by a flat key, interference fit, and set screw. This structure has significant drawbacks: under continuous high-frequency alternating loads of tens of thousands of revolutions per minute, slight slippage is likely to occur between the eccentric block and the main shaft, and the eccentricity gradually drifts, leading to a decrease in excitation force; the connecting parts are prone to loosening and failure under long-term alternating stress; assembly gaps will exacerbate rotational imbalance, resulting in high vibration and noise of the entire machine; the split structure has a large number of parts and a complicated assembly process.

[0006] The second type is a simple integral eccentric shaft structure: a single eccentric cylindrical solid is set in the middle of the main shaft. This eccentric block is an approximately cylindrical rotating body with obvious sharp edges. When the eccentric shaft rotates at high speed in the lubricating oil cavity inside the vibrator housing, the solid structure will strongly agitate the lubricating grease inside the housing, resulting in large oil loss and generating a large amount of agitation heat; the temperature rise of the components is significant, which can easily cause grease failure and bearing overheating and wear. At the same time, stress concentration exists at the sharp edges, which is prone to fatigue cracks under long-term high-frequency centrifugal loads, resulting in a short service life of the components.

[0007] In addition, the traditional eccentric structure lacks a reasonable fluid flow guide shape design, resulting in poor flow of lubricating oil inside the vibrator and poor oil supply conditions in the bearing area, which further limits the duration of continuous high-frequency operation of the vibrator. Summary of the Invention

[0008] This invention addresses the technical shortcomings of existing vibratory rods, such as poor structural adaptability, rapid seal failure, eccentric shaft wear, low equipment durability, lack of standardized assembly processes, lack of specifications for construction in irregular areas, and unstable concrete forming quality. The purpose of this invention is to solve the problems in the prior art and provide a high-frequency hydraulic vibratory rod and its assembly method.

[0009] The technical solution of the present invention is: a high-frequency hydraulic vibrator, comprising a vibrating shell assembly, a hydraulic power transmission assembly, a hydraulic pipeline protection assembly, and an eccentric excitation assembly; Furthermore, the hydraulic power transmission assembly and the eccentric vibration assembly are detachably assembled inside the vibratory housing assembly; the hydraulic pipeline assembly is connected to the hydraulic power transmission assembly.

[0010] Preferably, the hydraulic power transmission assembly includes a hydraulic drive motor, a cross-shaped transmission joint, and a transition connector. The hydraulic drive motor is connected to the eccentric vibration assembly via the cross-shaped transmission joint to achieve stable torque transmission.

[0011] Furthermore, the hydraulic drive motor includes a motor body, a front sealing end cover connected thereto, a drive gear shaft, and a driven gear shaft; the motor body has an oil inlet and an oil return port, and the drive gear shaft and the driven gear shaft mesh with each other and are built into the motor body; Furthermore, the front sealing end cover includes a stepped central through hole for accommodating the drive gear shaft, a blind hole located on one side of the central through hole for accommodating the driven gear shaft, a plurality of mounting holes located outside the central through hole for connecting the motor body, a plurality of pin holes, and an oblique hole that runs through the entire cover and communicates with the central through hole.

[0012] Furthermore, the oblique hole is directly drilled and formed obliquely on the end face of the front cover, and the machining is completed in one step; the oblique hole directly connects the shaft end lubrication cavity and the main oil return cavity.

[0013] Furthermore, the eccentric excitation assembly includes an eccentric block, which comprises an eccentric spindle and an eccentric block body integrally formed at the middle position of the eccentric spindle.

[0014] Furthermore, the eccentric spindle extends outward from both ends along the axial direction to form shaft extension sections, and each shaft extension section is provided with an external threaded connection structure at its end.

[0015] Furthermore, the eccentric block body is generally cylindrical, and the outer contour of the eccentric block body is symmetrically provided with concave arc-shaped relief surfaces on both sides, with a reinforcing rib in the middle of the two relief surfaces; the two ends of the eccentric block body have smooth transition arc surfaces and are connected to the eccentric main shaft as an integral structure; the center of gravity of the eccentric block body is deviated from the central axis of the eccentric main shaft, forming an eccentric structure.

[0016] Preferably, the eccentric vibration assembly further includes a bearing support structure, an axial limiting and locking structure, and a transmission connection joint. The two ends of the eccentric block are radially positioned by the bearing support structure and are limited to high-speed rotation without swaying by the axial limiting and locking structure. High-frequency centrifugal vibration force is generated by continuous rotation relying on hydraulic power.

[0017] Furthermore, the bearing support structure of the eccentric vibration assembly includes two sets of end bearing rings, four bearings and bearing spacers. Two bearings are symmetrically mounted on the journals at both ends of the eccentric block, and bearing spacers are placed between the two bearings. The two sets of end bearing rings are respectively attached to the outer sides of the bearings at both ends to achieve radial limiting support.

[0018] Furthermore, the axial limiting and locking structure includes a front bearing positioning retaining ring, a rear bearing positioning retaining ring, and a reverse thread nut. The front and rear positioning retaining rings respectively fit against the end faces of the bearings at both ends, and the reverse thread nut locks the rear shaft head of the eccentric block, forming a bidirectional axial limiting structure to suppress axial movement during high-speed rotation.

[0019] Furthermore, it also includes a double-layer sealing protection component, which includes a front seal and a rear seal. The front seal and the rear seal are located at both ends of the transition connection connector. The front seal and the rear seal are segmented independent sealing structures, which respectively block the intrusion of external concrete slurry and the leakage of internal hydraulic oil, thereby achieving bidirectional sealing protection.

[0020] Preferably, the vibratory housing assembly includes a vibratory housing and a bent connecting pipe, wherein the vibratory housing and the bent connecting pipe are fixedly connected and form a fixed bending angle of 45°.

[0021] Preferably, the hydraulic pipeline protection component includes an independent inlet oil pipeline, an outlet oil pipeline, and an external protective hose. The inlet oil pipeline and the outlet oil pipeline are respectively connected to the inlet and outlet oil ports of the hydraulic drive motor to form a closed-loop hydraulic circulation circuit, and the external protective hose completely covers the oil circuit to achieve protection.

[0022] Furthermore, the vibratory shell is a square shell structure, and the bent connecting pipe is a 45° vibratory rod connecting bend. The square shell and the 45° connecting bend are locked and positioned by a clamp locking assembly, a positioning screw and a positioning cover plate, ensuring a firm connection without relative rotation.

[0023] The present invention has the following beneficial effects: (1) The present invention opens an oblique hole in the front sealing end cover of the hydraulic drive motor. The oblique hole directly connects the shaft end lubrication cavity and the main return oil cavity. It is obliquely connected without a narrow throttling channel, resulting in a larger oil flow cross section and extremely low flow resistance. The internal leakage oil seeping out of the gear meshing gap and the bearing lubricating hot oil can quickly flow into the main return oil circuit through the oblique hole, release the pressure in the lubrication cavity in real time, maintain the low pressure environment inside the oil seal, greatly reduce the pressure on the oil seal, and suppress the problem of oil seepage and leakage at the shaft head during high-frequency operation of the vibrating rod from the root. The sealing reliability is significantly better than the existing shaft core internal leakage channel structure.

[0024] (2) The integrated eccentric block used in this invention is used as the excitation source. The double bearing support structure is symmetrically arranged at both ends. It is matched with spacer ring and end bearing ring to achieve precise radial positioning. The front and rear positioning retaining rings are used in conjunction with the reverse thread locking nut to form a bidirectional axial positioning. The reverse thread is opposite to the rotation direction to achieve self-tightening and anti-loosening during operation, which completely solves the problem of high-speed movement and ensures continuous and stable excitation force. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the structure of the present invention. Figure 2 Exploded view of the present invention Figure 3 and Figure 4 This is a perspective view of the hydraulic motor in this invention. Figure 5 This is a perspective view of the hydraulic motor in this invention without the motor body installed. Figure 6 This is a front view of the front sealing end cap in this invention. Figure 7 This is a perspective view of the front sealing end cap in this invention. Figure 8 This is a cross-sectional view of the front sealing end cap in this invention. Figure 9 This is a front view of the eccentric block in the present invention. Figure 10 This is a top view of the eccentric block in this invention. Figure 11 This is a three-dimensional view of the eccentric block in this invention. Detailed Implementation

[0026] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0027] The terminology used in the embodiments of this invention is for the purpose of describing particular embodiments only and is not intended to limit the invention. The singular forms “a,” “the,” and “the” used in the embodiments of this invention and the appended claims are also intended to include the plural forms, unless the context clearly indicates otherwise. “Multiple” generally includes at least two, but does not exclude the inclusion of at least one.

[0028] It should be understood that the term "and / or" used in this article is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.

[0029] Depending on the context, the words “if” or “suppose” as used here can be interpreted as “when” or “in response to determination” or “in response to detection.” Similarly, depending on the context, the phrases “if determination” or “if detection (of the stated condition or event)” can be interpreted as “when determination” or “in response to determination” or “when detection (of the stated condition or event)” or “in response to detection (of the stated condition or event).”

[0030] It should also be noted that the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a product or system comprising a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a product or system. Without further limitation, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the product or system that includes said element.

[0031] like Figure 1 and Figure 2 As shown, a high-frequency hydraulic vibrator of the present invention includes a vibratory housing assembly 100, a hydraulic power transmission assembly 200, a hydraulic pipeline protection assembly 300, and an eccentric excitation assembly 400. In this embodiment, the hydraulic power transmission component 200 and the eccentric vibration component 400 are detachably assembled inside the vibratory housing component 100; the hydraulic pipeline component 300 is connected to the hydraulic power transmission component 200.

[0032] The vibratory shell assembly 100 in this embodiment includes a vibratory shell 101 and a bent connecting pipe 102. The vibratory shell 101 and the bent connecting pipe 102 are fixedly connected and form a fixed bending angle of 45°.

[0033] The vibratory housing 101 has a square housing structure, and the bent connecting pipe 102 is a 45° vibratory rod connecting bend. The square housing and the 45° connecting bend are locked and positioned by the clamp locking assembly 103, the positioning screw 104 and the positioning cover plate 105, and the connection is firm and there is no relative rotation.

[0034] In this embodiment, a square vibratory shell is used in conjunction with an integrated 45° connecting bend to form a fixed 45° bend working end, breaking through the limitations of traditional straight bar vertical operation. It can be obliquely extended into the inside corners of various structures and narrow gaps between steel bars, completely eliminating the blind spot of vibration. The connection between the shell and the bend is secured by a triple locking and positioning of clamps, screws, and cover plates, ensuring no loosening or relative rotation during operation and strong structural stability.

[0035] The hydraulic power transmission assembly 200 in this embodiment includes a hydraulic drive motor 201, a cross-type transmission joint 202, and a transition connection connector 203. The hydraulic drive motor 201 is connected to the eccentric vibration assembly 400 through the cross-type transmission joint 202 to achieve stable torque transmission.

[0036] refer to Figures 3 to 8 As shown, the hydraulic drive motor 201 includes a motor body 21, a front sealing end cover 22 connected thereto, a drive gear shaft 23, and a driven gear shaft 24; the motor body 21 has an oil inlet 211 and an oil return port 212, and the drive gear shaft 23 and the driven gear shaft 24 mesh with each other and are built into the motor body 21.

[0037] In this embodiment, the front sealing end cover 22 includes a stepped central through hole 221 for accommodating the drive gear shaft 23, a blind hole 222 located on one side of the central through hole 221 for accommodating the driven gear shaft 24, a plurality of mounting holes 223 located outside the central through hole 221 for connecting the motor body 21, a plurality of pin holes 224, and an oblique hole 225 that runs through the entire cover and communicates with the central through hole 221.

[0038] In this embodiment, the cross-drive joint 202 is connected to the drive gear shaft 23. One end of the drive gear shaft 23 extends into the central through hole 221, and the driven gear shaft 24 is installed in the blind hole 222. The drive gear shaft 23 and the driven gear shaft 24 mesh with each other. Under the action of the oil inlet pipe 301 and the oil return pipe 302 in the hydraulic pipeline assembly 300, they respectively connect to the oil inlet and oil return ports of the hydraulic drive motor 201 to form a closed-loop hydraulic circulation circuit, thereby enabling it to rotate at high speed.

[0039] In this embodiment, the oblique hole 225 directly connects the shaft end lubrication chamber and the main return oil chamber. The oblique through-hole has no narrow throttling channel, resulting in a larger oil flow cross section and extremely low flow resistance. The internal leakage oil and bearing lubricating hot oil seeping out from the gear meshing gap between the drive gear shaft 23 and the driven gear shaft 24 can quickly flow into the main return oil circuit through the oblique hole 225, releasing the pressure in the lubrication chamber in real time and maintaining a low-pressure environment inside the oil seal. This significantly reduces the pressure on the oil seal and fundamentally suppresses the problem of oil seepage and leakage at the shaft end during high-frequency operation of the vibrator. The sealing reliability is significantly better than the existing shaft core internal leakage channel structure.

[0040] In this embodiment, the directional oil flow formed by the oblique hole 225 allows the main return low-pressure oil to enter the shaft end bearing cavity in a small amount in the reverse direction, continuously forming a complete lubricating oil film on the drive gear shaft, bearing, and oil seal lip, thus avoiding dry friction during high-speed rotation.

[0041] In addition, the bearings and gears generate a lot of heat when the vibrator is running at high frequency continuously; the 225 oblique hole has strong flow capacity, hot oil is discharged quickly, heat exchange efficiency is higher, oil seal high temperature aging and bearing high temperature pitting risk are reduced, continuous operation time is increased, and it is suitable for high frequency vibrators under long-term heavy load conditions.

[0042] The present invention also includes a double-layer sealing and protection component 500, which includes a front seal 501 and a rear seal 502. The front seal 501 and the rear seal 502 are disposed at both ends of the transition connector 203. The front seal 501 and the rear seal 502 are segmented independent sealing structures, which respectively block the intrusion of external concrete slurry and the leakage of internal hydraulic oil, thereby achieving bidirectional sealing and protection.

[0043] The double-layer sealing protection component 500 of the present invention adopts a front and rear segmented independent sealing structure. The front seal prevents external cement slurry and alkaline water vapor from entering the equipment, while the rear seal prevents internal high-pressure hydraulic oil from leaking out. It provides bidirectional zoned protection, with precise sealing dimensions and reasonable pre-compression, adapting to the high-frequency vibration conditions of the equipment and significantly improving sealing durability.

[0044] The hydraulic pipeline protection component 300 in this embodiment includes an independent oil inlet pipeline 301, an oil return pipeline 302, and an external protective hose 303. The oil inlet pipeline 301 and the oil return pipeline 302 are respectively connected to the oil inlet and return ports of the hydraulic drive motor 201 to form a closed-loop hydraulic circulation circuit. The external protective hose 303 completely covers the oil circuit to achieve protection.

[0045] The hydraulic pipeline protection component 300 in this embodiment adopts an independent inlet and return oil pipeline design to form a closed-loop hydraulic circulation system, ensuring smooth oil supply and return and stable pressure. It is externally fitted with a large-size protective hose to completely cover the oil circuit and prevent pipeline wear, bending and damage. Both ends of the pipeline are equipped with special rubber seals to effectively prevent dust and water when not in use, and extend the service life of the oil circuit.

[0046] like Figures 9 to 11 As shown, the eccentric vibration assembly 400 in this embodiment includes an eccentric block 600, a bearing support structure 401, an axial limiting and locking structure 402, and a transmission connection joint 403. The two ends of the eccentric block 600 are radially positioned by the bearing support structure 404, and the axial limiting and locking structure 402 achieves high-speed rotation without swaying and limiting. It generates high-frequency centrifugal vibration force by continuously rotating with hydraulic power.

[0047] The eccentric block 600 in this embodiment includes an eccentric main shaft 601 and an eccentric block body 602 integrally formed in the middle of the eccentric main shaft.

[0048] The eccentric spindle 601 extends outward from both ends along the axial direction to form shaft extension sections, and each shaft extension section is provided with an external threaded connection structure 603 at its end.

[0049] The eccentric block body 602 is generally cylindrical, and the outer contour of the eccentric block body 602 is symmetrically provided with concave arc-shaped relief surfaces 621 on both sides, with a reinforcing rib 622 in the middle of the two relief surfaces; the two ends of the eccentric block body 602 are smoothly transitioned to arc surfaces and are connected to the eccentric main shaft 601 as an integral structure; the center of gravity of the eccentric block body 602 is offset from the central axis of the eccentric main shaft 601, forming an eccentric structure.

[0050] In this embodiment, the size of the arc-shaped clearance surface 621 determines the size of the reinforcing rib 622, and the size of the arc-shaped clearance surface 621 and the reinforcing rib 622 determine the fundamental source of the excitation force and amplitude of the entire eccentric block assembly.

[0051] The structural principle of the eccentric block body 602 in this invention is as follows: The eccentric block body 602 has a symmetrical large-area concave hollow relief surface 621, which causes the mass on both sides of the rotation axis to be asymmetrical, forming a fixed eccentricity e and eccentric mass m, resulting in an eccentricity Me=me; when the hydraulic motor drives the eccentric block 600 to rotate at high speed, the eccentric mass performs circular motion and continuously outputs a periodic centrifugal excitation force F, where F=meω 2 In this formula, m is the eccentric mass of the eccentric block; e is the eccentricity (the distance from the center of mass of the eccentric block to the center of rotation); and ω is the angular velocity of the motor (ω=2πn / 60, where n is the motor speed).

[0052] According to the above formula, the core determining factors of the vibratory rod's amplitude are the eccentric mass *m* and the eccentricity *e* of the eccentric block. The larger the product of these two factors, *m·e*, the higher the amplitude. When the eccentric block parameters remain unchanged, the overall amplitude of the machine is basically constant. By changing the eccentric block counterweight or eccentricity, in this embodiment, the vibration amplitude can be adjusted by changing the dimensions of the clearance surface 621 and the reinforcing rib 622. In this embodiment, the excitation force is transmitted to the vibratory rod's housing through the bearings at both ends, causing the housing to generate high-frequency circular vibration, which is the power source for compacting concrete.

[0053] The deeper the clearance surface 621, the more material is removed, the larger the eccentric mass m, the larger the eccentricity e, and the larger the eccentricity Me, resulting in a larger overall vibration amplitude of the vibrator at the same rotation speed. Conversely, a smaller amount of hollowing out results in a smaller amplitude, which can be adapted to vibrating in fine and narrow areas. Therefore, adjusting the size of the clearance surface 621 can adjust the amplitude.

[0054] If the eccentric block moves axially, the rotation center shifts, and the eccentricity changes dynamically, the amplitude will fluctuate and the equipment will make abnormal noises. The front and rear retaining rings and the reverse thread nut limiting structure of this invention fix the rotation center of the eccentric block to ensure that the amplitude is uniform throughout the entire process.

[0055] In this invention, the eccentric block 600 is a high-speed rotating component. The avoidance surface 621 will significantly weaken the bending and torsional stiffness of the cylindrical base, making it prone to torsional deformation and fatigue fracture under high-frequency centrifugal force of tens of thousands of revolutions per minute. The axially continuous reinforcing rib 622 significantly increases the moment of inertia of the component section by thickening the cross section, thereby enhancing the overall structural strength of the eccentric block 600, resisting alternating stress, and preventing high-speed rotational out-of-roundness and bending deformation.

[0056] In this embodiment, the bearing support structure 401 of the eccentric vibration assembly 400 includes two sets of end bearing rings 411 and bearing spacers 412. Two bearings 413 are symmetrically mounted on the journals at both ends of the eccentric block 600. Bearing spacers 412 are placed between the two bearings 413. The two sets of end bearing rings 411 respectively fit against the outer side of the two bearings 413 to achieve radial limiting support.

[0057] Furthermore, the axial limiting and locking structure 402 includes a front bearing positioning retaining ring 421, a rear bearing positioning retaining ring 422, and a reverse thread nut 423. The front and rear positioning retaining rings 421 respectively fit the end faces of the bearings 413 at both ends, and the reverse thread nut 423 locks the shaft head at the rear end of the eccentric block 600, forming a bidirectional axial limiting structure to suppress axial movement during high-speed rotation.

[0058] In this embodiment, an integrated eccentric block 600 is used as the excitation source. The two ends are symmetrically arranged with a double bearing support structure. The radial precision is achieved by using spacers and end bearing rings. The front and rear positioning retaining rings are used in conjunction with the reverse thread locking nut to form a bidirectional axial limit. The reverse thread is opposite to the rotation direction to achieve self-tightening and anti-loosening during operation, which completely solves the problem of high-speed movement and ensures continuous and stable excitation force.

[0059] In addition, the assembly method of the present invention includes the following steps: S1. Pre-assembly of eccentric vibration assembly: Precision pre-assembly of eccentric block, bearing, spacer, positioning retaining ring, and reverse thread nut, using a torque wrench for standard tightening, controlling the axial movement clearance of the eccentric shaft to ≤0.02mm; S2, Double-layer sealing assembly: Front and rear seals are press-fitted into the stepped grooves at both ends of the transition connector to ensure that the seals are free from twisting and displacement, and that the pre-compression amount meets the standard; S3. Power and housing assembly: Install the pre-assembled eccentric excitation assembly into the bent vibratory housing, connect the 45° bend pipe, and tighten it evenly diagonally using clamps and positioning screws. Install the positioning cover plate for limiting the position. S4. Hydraulic pipeline assembly: Connect the inlet and return oil pipes to the hydraulic motor oil port, externally install a large protective hose, and assemble rubber seals at both ends; S5. Vibration damping component assembly: Install high-damping vibration damping blocks at the rear of the equipment, and tighten them symmetrically with standard bolts and nuts. Manually check for looseness and misalignment. S6. Complete machine inspection and debugging: Conduct hydraulic pressure holding leakage detection and no-load vibration test to confirm that there is no leakage in the seal, the vibration is uniform and stable, and there is no abnormal noise or movement, and complete the assembly.

[0060] This invention features a proprietary precision assembly process that abandons the traditional experience-based assembly model. It adopts a standardized process of graded torque locking, precise gap control, step-by-step assembly, and whole-machine testing to ensure that each piece of equipment has uniform assembly precision and consistent performance.

[0061] In addition, by limiting the standard torque of each locking structure, structural stress deformation caused by excessive tightness and vibration loosening caused by excessive looseness are avoided. At the same time, the equipment's sealing performance and vibration stability are ensured to meet the standards through no-load and pressure holding tests, resulting in strong consistency and high yield in mass production.

[0062] The oblique hole of this invention is opened in the fixed front sealing end cover, forming an oblique large flow cross section pressure relief channel with low flow resistance, quickly releasing the pressure in the shaft end lubrication cavity and preventing oil seal leakage; it forms a circulating lubrication oil channel, continuously cooling and lubricating the bearings and oil seals, greatly extending the life of vulnerable parts; the front sealing end cover is directly drilled and formed, making processing, assembly, and maintenance easier and reducing production costs; it buffers instantaneous impact pressure and automatically discharges air from the cavity, adapting to the high-frequency alternating impact conditions of the vibrator; the pressure relief oil is integrated into the main return oil circuit, eliminating the need for an external drain pipe, making the overall structure of the vibrator simpler and more compact.

[0063] The above description is merely a preferred embodiment of the present invention and is not intended to limit the scope of the invention. All equivalent changes and modifications made in accordance with the scope of the claims of this invention should fall within the technical scope of this invention.

Claims

1. A high-frequency hydraulic vibrator, characterized in that: This includes the vibratory housing assembly, the hydraulic power transmission assembly, the hydraulic pipeline protection assembly, and the eccentric vibration assembly; The hydraulic power transmission assembly and the eccentric vibration assembly are detachably assembled inside the vibratory housing assembly; the hydraulic pipeline assembly is connected to the hydraulic power transmission assembly; The hydraulic power transmission assembly includes a hydraulic drive motor, a cross-type transmission joint, and a transition connector. The hydraulic drive motor is connected to the eccentric excitation assembly through the cross-type transmission joint to achieve stable torque transmission. The hydraulic drive motor includes a motor body, a front sealing end cover connected thereto, a drive gear shaft, and a driven gear shaft; the motor body has an oil inlet and an oil return port, and the drive gear shaft and the driven gear shaft mesh with each other and are built into the motor body; The front sealing end cover includes a stepped central through hole for accommodating the drive gear shaft, a blind hole located on one side of the central through hole for accommodating the driven gear shaft, multiple mounting holes for connecting the motor body located outside the central through hole, multiple pin holes, and an oblique hole that runs through the entire cover and communicates with the central through hole. The eccentric vibration assembly includes an eccentric block, which comprises an eccentric spindle and an eccentric block body integrally formed in the middle of the eccentric spindle. The eccentric spindle extends outward at both ends along the axial direction to form shaft extension sections, and each shaft extension section is provided with an external thread connection structure at its end.

2. The high-frequency hydraulic vibrator according to claim 1, characterized in that: The oblique hole is directly drilled and formed obliquely on the end face of the front cover, and the machining is completed in one step; the oblique hole directly connects the shaft end lubrication cavity and the main oil return cavity.

3. The high-frequency hydraulic vibrator according to claim 1, characterized in that: The eccentric block body is generally cylindrical, with concave arc-shaped relief surfaces symmetrically arranged on both sides of the outer contour of the eccentric block body, and a reinforcing rib in the middle of the two relief surfaces; the two ends of the eccentric block body have smooth transition arc surfaces and are connected to the eccentric main shaft as an integral structure; the center of gravity of the eccentric block body is offset from the central axis of the eccentric main shaft, forming an eccentric structure.

4. The high-frequency hydraulic vibrator according to claim 2, characterized in that: The eccentric vibration assembly also includes a bearing support structure, an axial limiting and locking structure, and a transmission connection joint. The two ends of the eccentric block are radially positioned by the bearing support structure and are limited to high-speed rotation without swaying by the axial limiting and locking structure. It generates high-frequency centrifugal vibration force by continuously rotating with hydraulic power.

5. The high-frequency hydraulic vibrator according to claim 4, characterized in that: The bearing support structure of the eccentric vibration assembly includes two sets of end bearing rings, four bearings and bearing spacers. Two bearings are symmetrically mounted on the journals at both ends of the eccentric block, and bearing spacers are placed between the two bearings. The two sets of end bearing rings are respectively attached to the outer sides of the bearings at both ends to achieve radial limiting support.

6. The high-frequency hydraulic vibrator according to claim 4, characterized in that: The axial limiting and locking structure includes a front bearing positioning retaining ring, a rear bearing positioning retaining ring, and a reverse thread nut. The front and rear positioning retaining rings respectively fit against the end faces of the bearings at both ends, and the reverse thread nut locks the rear shaft head of the eccentric block, forming a bidirectional axial limiting structure to suppress axial movement during high-speed rotation.

7. The high-frequency hydraulic vibrator according to claim 6, characterized in that: It also includes a double-layer sealing protection component, which includes a front seal and a rear seal. The front seal and the rear seal are located at both ends of the transition connection connector. The front seal and the rear seal are segmented independent sealing structures, which respectively block the intrusion of external concrete slurry and the leakage of internal hydraulic oil, thereby achieving bidirectional sealing protection.

8. The high-frequency hydraulic vibrator according to claim 1, characterized in that: The vibratory shell assembly includes a vibratory shell and a bent connecting pipe, which are fixedly connected and form a fixed bending angle of 45°.

9. The high-frequency hydraulic vibrator according to claim 1, characterized in that: The hydraulic pipeline protection component includes an independent inlet oil pipeline, an outlet oil pipeline, and an external protective hose. The inlet oil pipeline and the outlet oil pipeline are respectively connected to the inlet and outlet oil ports of the hydraulic drive motor to form a closed-loop hydraulic circulation circuit. The external protective hose completely covers the oil circuit to achieve protection.

10. The high-frequency hydraulic vibrator according to claim 8, characterized in that: The vibratory shell is a square shell structure, and the bent connecting pipe is a 45° vibratory rod connecting bend. The square shell and the 45° connecting bend are locked and positioned by a clamp locking assembly, positioning screws and positioning cover plate, and the connection is firm and there is no relative rotation.

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