A high-frequency micro-amplitude exciter for medium-large workpiece vibration-assisted laser cladding

Abstract

The application discloses a high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium-large workpieces. The parallel cylinders in the exciter are coaxially arranged with equal phase difference. A plurality of partitions are arranged in each cylinder unit with equal phase. The partitions of adjacent cylinder units are arranged with equal phase difference. A plurality of steel balls in each cylinder unit are sequentially thrown to impact the inner wall of the cylinder to generate micro-amplitude vibration. The m*a steel balls in the m cylinders excite micro-vibration of m*a Hz. The amplitude of the workpiece to be processed can be adjusted according to the need. The vibration frequency of the workpiece to be processed can be changed by replacing the number of cylinders and the corresponding installation angle of the cylinders or replacing the number of steel balls in the cylinders. The exciter is especially suitable for vibration-assisted laser cladding, grain refinement, stress release, homogeneous phase and obtaining forged state organization.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of mechanical vibration technology of exciter which can achieve 1200Hz and amplitude of 5μm to 50μm, in particular to the design of cylinder based on random falling of steel ball and the design of special-shaped spring with high natural frequency. BACKGROUND

[0002] Laser cladding is a commonly used additive remanufacturing technology, which has good formability, dense structure, grain refinement, and small heat-affected zone, and is widely used in additive manufacturing and remanufacturing of parts, surface strengthening. However, due to the large temperature gradient and fast solidification of the molten pool, it will lead to uneven distribution of elements and hard phase additives, difficulty in gas discharge and large residual stress, etc., which reduces the performance of the cladding layer. Therefore, it is urgent to improve the process to optimize the performance of the cladding layer according to the causes of the defects of the cladding layer.

[0003] It has been proved that introducing mechanical vibration into casting or welding process is an effective auxiliary process to break up dendrites, refine grains, stir the molten pool, promote the uniform distribution of elements and hard phases, and gas discharge, and significantly improve the performance of the workpiece. Since the solidification rate of laser cladding can be as high as 10 6 ℃ / s, and the molten pool is generally less than 2mm, the existing mechanical vibrator cannot produce high enough frequency and low enough amplitude without affecting the surface morphology of the cladding layer during the laser cladding process, so there is an urgent need for high-frequency micro-amplitude exciter above 800Hz and amplitude of 5μm to 50μm in engineering. The present application is designed with 1200Hz as the parameter, which can achieve the expected purpose after calculation.

[0004] At present, among several commonly used types of mechanical vibration exciters, there are characteristics that are not suitable for laser cladding process: eccentric and centrifugal mechanical vibration structure is simple but low frequency and large waveform distortion;

[0005] Electro-hydraulic type has large amplitude but narrow frequency range (100-150Hz);

[0006] Hydraulic and pneumatic type has small amplitude and frequency;

[0007] Electromagnetic and magnetostrictive type has high frequency (up to 10000Hz) and small amplitude (≤50μm) but is only suitable for small mass and size workpieces.

[0008] In addition, the current mechanical vibration exciter needs to fix the workpiece on the working plane of the exciter, which is difficult to use for the surface of the rotary body under the condition of circumferential cladding requiring mechanical vibration assisted cladding.

[0009] Therefore, developing high-frequency micro-amplitude mechanical vibration exciter for laser cladding of medium and large rotary parts is beneficial to improve the performance of laser cladding coating of rotary body. SUMMARY

[0010] To solve the technical problems proposed in the background art, the present application provides a high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium and large workpieces. The exciter can generate high-frequency micro-amplitude mechanical vibrations of 1200 Hz and 5-50 microns, and mechanically provides vibrations to achieve the technical purpose of providing mechanical vibration-assisted process for laser cladding of medium and large rotary bodies.

[0011] To achieve the above-mentioned purpose, the present application adopts the following technical solutions:

[0012] A high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium and large workpieces, comprising:

[0013] A base plate located at the bottom of the entire exciter;

[0014] A vibration receiving plate arranged horizontally on the base plate, one end of which is hinged to the base plate hinge arranged at one end of the base plate, and the other end is connected to the base plate through a high natural frequency spring;

[0015] A rotating drum assembly installed on the vibration receiving plate adjacent to one end of the high natural frequency spring through a rotating drum support, the rotating drum assembly is composed of a plurality of cylindrical units with the same radius which are axially connected to each other, from the cylindrical unit at one end of the rotating drum assembly to the cylindrical unit at the other end, connected in the same direction in the circumferential direction with the same angle interval through the circumferential positioning and torque transmission mechanism,

[0016] Each of the cylindrical units contains a steel ball with the same radius and material;

[0017] An equal angle of n baffles with a certain angle to the axis of the cylindrical unit and a radial width greater than the radius of the steel ball is fixed in the inner wall of each cylindrical unit, and the baffles divide the cylindrical unit into n regions;

[0018] When the rotating drum rotates at a constant speed, the steel ball falls from one baffle to the inner wall of the cylindrical unit, and the impact force is converted into displacement by the high natural frequency spring and transmitted to the workpiece through the vibration receiving plate and the workpiece clamp installed on the vibration receiving plate.

[0019] From the cylindrical unit at one end of the rotating drum assembly to the cylindrical unit at the other end, connected in the same direction in the circumferential direction with a certain angle interval through the circumferential positioning and torque transmission mechanism.

[0020] The rotating drum assembly includes a plurality of cylindrical units, a front end cover and a rear end cover, the plurality of cylindrical units are axially connected to form a cylindrical string, one end of the cylindrical string is connected to the front end cover, and the other end is connected to the rear end cover;

[0021] One end of the cylinder unit is provided with a first cylinder flange, and the other end is provided with a second cylinder flange; the first cylinder flange is provided with a cylindrical protrusion coaxial with the first cylinder flange, and the second cylinder flange is provided with a cylindrical recess coaxial with the second cylinder flange; the cylindrical protrusion and the cylindrical recess are axially limited between the cylinder units;

[0022] The circumferential positioning and torque transmission mechanism includes a first cylinder flange arranged on one side of the cylinder unit, a pair of first positioning columns arranged on the first cylinder flange and opposite to each other by 180°, and ten pairs of first positioning holes arranged on the second cylinder flange on the other side of the cylinder unit and opposite to each other by 180°, and one of the first positioning holes is present in a certain angle of rotation relative to the vertical reference surface of the cylinder unit;

[0023] A second positioning column is arranged on the front end cover flange, and the front end cover flange is connected with the first positioning hole on the cylinder unit through the second positioning column;

[0024] A second positioning hole is arranged on the rear end cover flange, and the rear end cover flange is connected with the first positioning hole through the second positioning hole.

[0025] The front end cover includes a front end cover flange, a front end cover shaft, and a cylindrical protrusion, wherein,

[0026] The other side of the front end cover flange is provided with a front end cover shaft;

[0027] The rear end cover includes a rear end cover flange, a rear end cover shaft, and a rear end cover cylindrical recess, wherein,

[0028] The other side of the rear end cover flange has a rear end cover shaft, the outer diameter of the rear end cover is larger than that of the cylinder unit, and the rear end cover has a rear end cover bolt hole.

[0029] The high natural frequency spring is a rigid arc-shaped shaft segment with a certain curvature, the end of the rigid arc-shaped shaft segment is provided with a pin hole, and the rigid arc-shaped shaft segment is installed directly below the rotating drum assembly; the natural frequency of the rigid arc-shaped shaft segment is above 1300 Hz, and the rigidity is not less than 14.3 kN / mm, which can output a micron-level amplitude to meet the use requirements of the vibration test bench.

[0030] The two ends of the rotating drum support are respectively provided with a front end cover and a rear end cover, a rolling bearing is installed in the rotating drum support, the rotating drum support and the workpiece clamp are both installed on a vibration receiving plate, the outer ring of the rear end cover is connected with a gear ring, and the gear ring is connected with a transmission system composed of a speed reducer, a motor and a frequency converter to provide torque for the rotating drum assembly.

[0031] The tooth thickness thinning amount of the gear ring is 2-8 levels, and the corresponding meshing gap is 0.13-0.26 mm, which can increase the meshing impact to one side in the meshing process, can obtain additional high-frequency micro-amplitude vibration in the horizontal direction, and thus can obtain two-dimensional high-frequency micro-amplitude vibration.

[0032] Advantages:

[0033] The high-frequency micro-amplitude exciter for the vibration-assisted laser cladding of medium and large workpieces has the following advantages compared with the prior art:

[0034] First, the present application uses multiple parallel and equal phase difference cylinder units axially connected to form a cylinder string, and a steel ball with the same size and material is arranged in each cylinder unit. High-frequency micro-amplitude mechanical vibration is generated by the impact of the steel ball in the cylinder unit on the inner wall of the cylinder unit, which meets the actual needs of the rotation and vibration of the rotary body during the laser cladding process of the medium and large rotary body, thereby refining the grain, homogenizing the element and hard phase distribution, reducing the residual stress, improving the performance of the cladding layer, and having good economic efficiency and popularization value.

[0035] Second, the present application designs a high natural frequency spring, which is a rigid arc-shaped shaft segment with a certain curvature. The end of the rigid arc-shaped shaft segment is provided with a pin hole and is installed directly below the rotating drum assembly. The rigid arc-shaped shaft segment has extremely strong bearing capacity, high enough stiffness and natural frequency, and the advantages of high frequency and micro-amplitude response which are lacking in various existing widely used springs.

[0036] Third, the tooth thickness reduction of the gear ring is 2-8 levels, and the corresponding meshing gap is 0.13-0.26mm. During the meshing process of the gear ring and the gear, the meshing impact can be increased to one side, and additional high-frequency micro-amplitude vibration can be obtained in the horizontal direction, thereby obtaining two-dimensional high-frequency micro-amplitude vibration. BRIEF DESCRIPTION OF DRAWINGS

[0037] Figure 1 is a schematic diagram of the high-frequency micro-amplitude exciter for the vibration-assisted laser cladding of medium and large workpieces of the present application;

[0038] Figure 2 is a structural schematic diagram of the high-frequency micro-amplitude exciter for the vibration-assisted laser cladding of medium and large workpieces of the present application;

[0039] Among them, 1 is a rotating drum assembly; 3 is a high natural frequency spring; 4 is a vibration receiving plate; 5 is a rotating drum support; 6 is a gear ring; 7 is a base plate;

[0040] Figure 3 is an exploded view of the cylinder assembly and the front and rear end cover assembly of the present application;

[0041] Among them, 11 is a cylinder unit; 12 is a front end cover; 13 is a rear end cover;

[0042] Figure 4 is a front view of the present application;

[0043] Wherein, 111 is the partition; 117 is the cylindrical recess;

[0044] Figure 5 is the A-A sectional view of Figure 4

[0045] Wherein, 112 is the first positioning column; 113 is the first positioning hole; 114 is the first cylindrical flange; 115 is the second cylindrical flange; 116 is the cylindrical protrusion;

[0046] Figure 6 is the first positioning hole schematic diagram of the present application;

[0047] Figure 7 is the left view of the front end cover of the present application;

[0048] Wherein, 121 is the front end cover positioning column; 122 is the front end cover flange; 123 is the front end cover cylindrical protrusion; 124 is the front end cover shaft;

[0049] Figure 8 is the front view of the rear end cover of the present application;

[0050] Wherein, 131 is the rear end cover positioning hole; 135 is the rear end cover bolt hole;

[0051] Figure 9 is the B-B sectional view of Figure 8

[0052] Wherein, 132 is the rear end cover flange; 133 is the rear end cover cylindrical recess; 134 is the rear end cover shaft;

[0053] Figure 10 is the front view of the high natural frequency spring of the present application;

[0054] Wherein, 31 is the connecting head; 32 is the limiting boss;

[0055] Figure 11 is the isometric view of the vibration receiving plate of the present application;

[0056] Wherein, 41 is the vibration receiving plate main body; 42 is the hinge; 43 is the first long slot hole; 44 is the second long slot hole; 45 is the mounting hole; 46 is the pin hole. DETAILED DESCRIPTION

[0057] ​​In order to make the technical solutions of the present application better understood by the people in the art, the technical solutions of the present application are described clearly and completely below in combination with the drawings of the present application. Based on the embodiments in the present application, other similar embodiments obtained by the people in the art without making creative efforts shall all belong to the scope of protection of the present application. In addition, the directional words mentioned in the following embodiments, such as "up", "down", "left", "right", "inner" and "outer", are only the directions of the drawings, therefore, the directional words used are used for illustration but not for limiting the present application.

[0058] Embodiment 1

[0059] Referring to Figures 1 to 4 A high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium-large workpieces, comprising:

[0060] A base plate 7 is located at the bottom of the entire exciter;

[0061] A vibration receiving plate 4 is arranged horizontally on the base plate 7, one end of which is hinged to a base plate hinge arranged at one end of the base plate 7, and the other end is connected to the base plate 7 through a high natural frequency spring 3;

[0062] A rotating drum assembly 1 is installed on the vibration receiving plate 4 through a rotating drum support 5 adjacent to one end of the high natural frequency spring 3, the rotating drum assembly 1 is composed of a plurality of cylindrical units 11 with the same radius which are axially connected to each other, from the cylindrical unit 11 at one end of the rotating drum assembly 1 to the cylindrical unit 11 at the other end, the cylindrical units 11 are connected to each other in the same direction through a circumferential positioning and torque transmission mechanism,

[0063] Specifically, each cylindrical unit contains a steel ball 2 with the same radius and material inside;

[0064] Specifically, n baffles 111 with a certain angle to the axis of the cylindrical unit and a radial width slightly larger than the radius of the steel ball 2 are fixed at equal angles in the inner wall of each cylindrical unit 11, for example, the radial width of the baffle is 1.1-1.5 times the radius r of the steel ball, the baffle 111 divides the cylindrical unit 11 into n regions;

[0065] Specifically, when the rotating drum assembly 1 rotates at a constant speed, the steel ball 2 falls from one baffle 111 to the inner wall of the cylindrical unit 11, and the impact force generated is converted into displacement by the high natural frequency spring 3 and transmitted to the workpiece through the vibration receiving plate 4 and the workpiece clamp installed on the vibration receiving plate 4.

[0066] Referring to Figure 3 From the cylindrical unit 11 at one end of the rotating drum assembly 1 to the cylindrical unit 11 at the other end, the cylindrical units 11 are connected to each other in the same direction through the circumferential positioning and torque transmission mechanism, R-r)πr2, where R is the inner wall radius of the cylindrical unit 11, r is the radius of the steel ball, and m is the number of the cylindrical unit 11.

[0067] Specifically, the rotating drum assembly 1 comprises a plurality of cylindrical units 11, a front end cover 12 and a rear end cover 13, m cylindrical units 11 are axially connected in series to form a cylindrical string, one end of the cylindrical string is connected to the front end cover 12, and the other end is connected to the rear end cover 13.

[0068] Referring to Figure 5 , one end of the cylindrical unit 11 is provided with a first cylindrical flange 114, and the other end is provided with a second cylindrical flange 115; the first cylindrical flange 114 is provided with a cylindrical protrusion 116 coaxial with the first cylindrical flange 114, and the second cylindrical flange 115 is provided with a cylindrical recess 117 coaxial with the second cylindrical flange 115; the cylindrical units 11 are axially limited and torque is transmitted through the cylindrical protrusion 116 and the cylindrical recess 117.

[0069] Referring to Figure 5 , Figure 6 , the circumferential positioning and torque transmission mechanism comprises a first cylindrical flange 114 arranged on one side of the cylindrical unit 11, a pair of first positioning columns 112 arranged on the first cylindrical flange 114 and opposite to each other by 180°, and ten pairs of first positioning holes 113 arranged on the second cylindrical flange 115 of the other side of the cylindrical unit 11, and the first positioning holes 113 are arranged at an angle of relative to the vertical reference plane of the cylindrical unit 11, where t is the thickness of the partition plate 111; is the angle of overlap with the vertical reference plane of the exciter when k times frequency is obtained; is the included angle between adjacent positioning holes, and if there is a partition plate between adjacent positioning holes, then the symbol “[]” means to take the integer part. Each pair of first positioning columns 112 and the mth pair of first positioning holes 113 cooperate to meet the requirement that adjacent cylindrical units are spaced apart by 2R-r)πr2 degrees in the same direction.

[0070] Referring to Figure 7 , the front end cover 12 comprises a front end cover flange 122, a front end cover shaft 124 and a cylindrical protrusion 123, the front end cover flange 122 and the first cylindrical flange 114 have the same shape, and the other side of the front end cover flange 122 is provided with the front end cover shaft 124.

[0071] Referring to Figure 8 , the rear end cover 13 comprises a rear end cover flange 132, a rear end cover shaft 134 and a rear end cover cylindrical recess 133, the other side of the rear end cover flange 132 has the rear end cover shaft 134, the outer diameter of the rear end cover 13 is greater than the outer diameter of the cylindrical unit 11, and the rear end cover has a rear end cover bolt hole 135. ​

[0072] Referring to Figure 9 , the high natural frequency spring 3 is a rigid arc-shaped shaft segment with a certain curvature, and has two end connecting heads 31 and a limiting boss 32 at both ends. The end of the rigid arc-shaped shaft segment is provided with a pin hole, and is installed below the rotating drum assembly 1 through an elastic pin. The connection relationship is φ30 H8 / m7. The rigid arc-shaped shaft segment has very strong bearing capacity (up to 300 kg, rigidity is not less than 14.3 kN / mm and natural frequency is above 1300 Hz), and has the advantages of high frequency response and micro deformation which are lacked by various springs (less than 500 Hz, 10 kN / mm) widely used at present.

[0073] Specifically, the rotating drum support 5 is respectively provided with a front end cover 12 and a rear end cover 13 at both ends. Rolling bearings are installed in the rotating drum support 5. The rotating drum support 5 and the workpiece clamp are both installed on the vibration receiving plate 4. The rear end cover 13 is connected with a gear ring 6. The gear ring 6 is connected with a transmission system composed of a speed reducer, a motor and a frequency converter to provide torque for the rotating drum assembly.

[0074] Specifically, the gear ring 6 has a tooth thickness thinning amount of 2-8 levels, and the corresponding meshing gap is 0.13-0.26 mm. During the meshing process of the gear ring gear, the meshing impact can be increased to one side, and additional high-frequency micro vibration can be obtained in the horizontal direction, so as to obtain two-dimensional high-frequency micro vibration.

[0075] Referring to Figure 10 , the vibration receiving plate 4 has a pair of hinges 42 at one end, which are hinged with the base plate 7 through pins. The vibration receiving plate body 41 is provided with a first long slot hole 43 and a second long slot hole 44 for respectively installing a workpiece clamp and an exciter, and a pair of mounting holes 45 for installing the high natural frequency spring 3. On the side surface perpendicular to the vibration receiving plate body 41 and the center line of the mounting hole 45, there are pin holes 46 for fixing the high natural frequency spring 3.

[0076] Specifically, the rotating speed of the cylinder unit 11 of the exciter is usually fixed. The output frequency is mainly changed by changing the number of cylinder units 11 and selecting the first positioning hole 113 between the cylinder units 11 corresponding to the number and the rear end cover positioning hole 131 of the rear end cover. The output amplitude is mainly changed by changing the density of the steel balls 2. The output frequency and amplitude can also be adjusted by changing the rotating speed. The ratio of the inner diameter of the cylinder unit 11 to the diameter of the steel ball 2 will affect the output frequency and amplitude.

[0077] Calculation feasibility

[0078] The steel balls in the cylinder undergo the process of separating from the inner wall of the cylinder, rolling on the partition plate, falling and colliding.

[0079] Steel ball in the cylinder, will along with the rotation of the cylinder to a certain height, will be along the partition plate rolling or sliding a certain distance, in the end of the partition plate with a certain speed to throw and impact the inner wall of the cylinder. In the process of force analysis of steel ball, it is assumed that there is no relative sliding between steel ball and the inner wall of the cylinder in the process of rising, and the friction between steel balls is ignored. When the steel ball reaches a certain position, it will move relative to the partition plate and the contact force with the inner wall of the cylinder is zero, it is assumed that the angle between the partition plate plane and the horizontal plane is α i , the angle between the centrifugal force direction of the i-th steel ball and the partition plate plane is θ i , the force analysis of steel ball, steel ball is subjected to gravity G, centrifugal force F, support force N of partition plate and friction force f N , support force N of adjacent steel ball b , the radius of the inner wall of the cylinder is R, the length is L, the angular velocity is ω, the radius of the steel ball is r, the mass is m b , the number is n b , the angle between the longitudinal symmetry line of the partition plate and the axis of the cylinder is The thickness of the partition plate is t, the width is w, and the friction coefficient is μ. The mechanical decomposition of the force of the steel ball along the long side of the partition plate downward, along the short side of the partition plate to the center of the cylinder and perpendicular to the partition plate plane is carried out, which is called "partition plate coordinate system". In Z direction, the steel ball has force balance, so only the force conditions in X and Y directions are analyzed:

[0080]

[0081] The angle α between the partition plate plane and the horizontal plane can be solved: i

[0082]

[0083] When the steel ball reaches the position where the contact force with the inner wall of the cylinder is zero, it will begin to roll along with the rotation of the cylinder, but since the width of the partition plate is only slightly larger than the radius of the steel ball, the steel ball will be thrown after rolling a short distance without sliding stage. In addition, the component velocity of the steel ball in the X axis of the partition plate coordinate system is large, the resultant force in the X axis is greater than that in the Z axis, the rolling distance is short, so the steel ball will not be subjected to the force of adjacent steel ball after rolling, and the friction force is approximately in the X axis direction. Let s be the displacement of the steel ball along the X direction of the partition plate coordinate system, the mechanical analysis is as follows:

[0084]

[0085] Based on the principle of pure rolling:

[0086]

[0087] Substitute the boundary conditions to solve the differential equation, Taylor expand and simplify the differential equation,

[0088] ​

[0089] Rolling distance s of the steel ball i Substitute to obtain rolling time t r Further, the position and speed of the steel ball when falling are obtained, the parabolic equation of the steel ball is obtained, the falling height and the speed v at the falling point are obtained in combination with the profile equation of the cylinder b And momentum, assuming that the collision time of the steel ball with the cylinder wall is 0.002s, using the impulse theorem, the collision force F exerted by the steel ball on the cylinder wall is known p . Set the spring stiffness k spr , then the displacement caused by one steel ball The output frequency f of one cylinder = n b 10 cylinders can output a frequency of 10f.

[0090] In Figure 1 , the spring top under the action of vertical force F, the linear displacement f of the force point in the vertical direction is obtained by applying Mohr integral y , so as to calculate the spring stiffness, and further to obtain the natural frequency of the spring reaches 1200Hz or more, which meets the use requirement of the exciter.

[0091] The above only details the preferred embodiment of the present application, but the present application is not limited to the above-mentioned embodiments, various changes can be made within the knowledge possessed by those skilled in the art without departing from the purpose of the present application, and various changes shall be included in the protection scope of the present application.

Claims

1. A high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium and large workpieces, characterized in that, include: The substrate is located at the very bottom of the entire exciter; A vibration receiving plate is arranged horizontally on the substrate. One end of the plate is hinged to a substrate hinge seat arranged at one end of the substrate, and the other end is connected to the substrate through a high natural frequency spring. The rotating cylinder assembly is mounted on the vibration support plate near one end of the high natural frequency spring via a rotating cylinder bracket. The rotating cylinder assembly is composed of multiple cylindrical units with the same radius connected axially in series. From the cylindrical unit at one end of the rotating cylinder assembly to the cylindrical unit at the other end, they are connected in pairs at the same angle in the same direction in the circumferential direction through a circumferential positioning and torque transmission mechanism. Each cylindrical unit contains a steel ball with the same radius and material. Each cylindrical unit has n partitions fixed at a certain angle to the inner wall of the cylindrical unit, with a radial width greater than the radius of the steel ball. The partitions divide the cylindrical unit into n regions. When the drum rotates at a constant speed, the steel ball falls from a partition to the inner wall of the cylinder in the cylindrical unit. The resulting impact force is converted into displacement by the high natural frequency spring and transmitted to the workpiece through the vibration support plate and the workpiece clamp mounted on the vibration support plate.

2. The high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium and large workpieces according to claim 1, characterized in that, The rotating drum assembly includes several cylindrical units, a front end cover, and a rear end cover. The several cylindrical units are axially connected in series to form a cylindrical string. One end of the cylindrical string is connected to the front end cover, and the other end is connected to the rear end cover. One end of the cylindrical unit is provided with a first cylindrical flange, and the other end is provided with a second cylindrical flange; the first cylindrical flange is provided with a cylindrical protrusion coaxial with the first cylindrical flange, and the second cylindrical flange is provided with a cylindrical recess coaxial with the second cylindrical flange; the cylindrical units are axially limited by the cylindrical protrusion and the cylindrical recess. The circumferential positioning and torque transmission mechanism includes: a first cylindrical flange disposed on one side of the cylindrical unit, a pair of first positioning pins disposed on the first cylindrical flange at 180° relative to each other, and ten pairs of first positioning holes disposed on the second cylindrical flange disposed on the other side of the cylindrical unit at 180° relative to each other, with one first positioning hole in each case when rotated a certain angle relative to the vertical reference plane of the cylindrical unit.

3. The high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium and large workpieces as described in claim 2, characterized in that, The front cover includes a front cover flange, a front cover shaft, and a cylindrical protrusion, wherein the front cover flange is provided with a front cover shaft on the other side; The rear end cover includes a rear end cover flange, a rear end cover shaft, and a cylindrical recess in the rear end cover, wherein, The other side of the rear cover flange has a rear cover shaft, the outer diameter of the rear cover is larger than that of the cylindrical unit, and there are rear cover bolt holes.

4. The high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium and large workpieces as described in claim 1, characterized in that, The high natural frequency spring is a rigid arc-shaped shaft segment with a certain curvature. The end of the rigid arc-shaped shaft segment has a pin hole and is installed directly below the rotating drum assembly. The natural frequency of the rigid arc-shaped shaft segment is above 1300Hz and the stiffness is not less than 14.3kN / mm. It can output micron-level amplitude to meet the requirements of vibration test bench.

5. The high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium and large workpieces as described in claim 1, characterized in that, The front end cover and the rear end cover are respectively installed at both ends of the rotary drum support. The rolling bearing is installed in the rotary drum support. The rotary drum support and the workpiece fixture are both installed on the vibration support plate. The outer ring of the rear end cover is connected to a gear ring. The gear ring is connected to the transmission system composed of the reducer, the motor and the frequency converter to provide torque for the rotary drum assembly.

6. The high-frequency micro-amplitude exciter for vibration-assisted laser cladding of medium and large workpieces as described in claim 5, characterized in that, The tooth thickness reduction of the gear ring is 2 to 8 levels, and the corresponding meshing clearance is 0.13 to 0.26 mm. During meshing, the meshing impact can be increased to one side, and additional high-frequency micro-amplitude vibration can be obtained in the horizontal direction, thereby obtaining two-dimensional high-frequency micro-amplitude vibration.

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