Two-dimensional power-driven decoupled arrangement type efficient environmental protection type vibrating pile hammer and parameter determination method thereof

Abstract

The present application belongs to the technical field of vibration pile driving (pulling), and discloses a two-dimensional power-driven decoupling arrangement type high-efficiency environmentally-friendly vibration pile hammer and a parameter determination method thereof. A linear vibration exciter group and a torsional vibration exciter group are arranged in single group or multiple groups respectively; the linear vibration exciter groups are synchronously operated; the torsional vibration exciter groups are synchronously operated; the linear vibration exciter groups and the torsional vibration exciter groups are arranged in a decoupling manner; the vibration exciters of the linear vibration exciter groups and the torsional vibration exciter groups are all composed of eccentric rotors driven by various power sources. The two-dimensional power source is adopted to realize the flexible vibration pile driving (pulling) function; the up-down vibration and the torsional vibration are simultaneously performed to meet the pile foundation depth requirement; the overall pile driving efficiency is significantly improved; the pile driving engineering cost is significantly reduced; effective pile driving can be realized in the hard soil condition; the power consumption is relatively reduced; the pile is not easy to deform or damage; and the dynamic load and noise transmitted to the surrounding environment of the pile are very small.

Description

Technical Field

[0001] This invention relates to the field of vibratory pile driving (extraction) technology, and in particular to a two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer and its parameter determination method. Background Technology

[0002] The application of pile foundations in various construction projects is becoming increasingly widespread, and vibratory pile hammers (including vibratory pile driving and vibratory pile extraction functions), as an indispensable pile foundation construction equipment, are bound to be used more and more extensively. Especially for wind power and photovoltaic projects in deserts, tidal flats, or mountains, as well as infrastructure construction projects such as buildings, roads, bridges, and airports, and construction projects such as offshore wind power or offshore operation platforms, the first step in the construction of these projects is the pile driving process, and the subsequent dismantling process requires the pile extraction process.

[0003] As the core equipment in vibratory pile driving / extraction technology, the performance of the vibratory pile hammer directly affects the efficiency and quality of pile driving / extraction. Existing conventional pile driving procedures are generally divided into hydraulically driven static pressure pile driving, impact pile driving, and vibratory pile driving. Among these, vibratory pile driving is the most common. The basic principle of most traditional vibratory pile driving or extraction methods involving vibratory pile hammers is: to generate a single-direction excitation force through a single exciter (i.e., an eccentric rotor driven by a power source such as a motor / hydraulic / pneumatic power source) or multiple exciters, thereby driving the vibratory pile hammer and pile to achieve linear vibration in a single direction. In other words, traditional pile driving and extraction methods all use one-dimensional power, achieving the vibratory pile driving and extraction function solely through a single-direction linear vibration trajectory. Research and practice have shown that this driving method has the following shortcomings:

[0004] 1) The pile depth cannot meet the project requirements;

[0005] 2) The overall efficiency of the piling process is low (i.e., the pile penetration rate is too low).

[0006] 3) Piles driven by conventional vibratory piling technology are difficult to extract later;

[0007] 4) High piling costs (for example, most photovoltaic piles in the desert must be filled with water before they can be driven to the required depth).

[0008] 5) Piling is more difficult in hard soil conditions;

[0009] 6) High power consumption;

[0010] 7) The pile itself is prone to deformation / damage;

[0011] 8) The dynamic load and noise transmitted to the surrounding environment of the pile are large (for onshore pile driving, it affects the health of surrounding residents or the safety of surrounding buildings or operating equipment; for offshore pile driving, it affects the health and reproduction of marine life).

[0012] To address the shortcomings of existing technologies, this invention proposes a two-dimensional power-driven, decoupled, high-efficiency, and environmentally friendly vibratory pile hammer. The aim is to achieve high efficiency, high quality, environmental friendliness, noise reduction, pile protection, energy saving, and easy pile extraction in pile foundation operations through innovative technologies such as innovative vibration modes (using two-dimensional power drive), redistribution of the coupled frictional force vector between the pile and soil, optimization of system parameter determination methods, and improved vibration reduction and noise reduction effects. This provides a completely new solution for pile foundation engineering. Summary of the Invention

[0013] To overcome the shortcomings of existing technologies, this invention proposes a two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer.

[0014] The technical solution of the present invention is as follows: A two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer includes a linear vibration exciter group and a torsional vibration exciter group; the linear vibration exciter group and the torsional vibration exciter group are arranged in single or multiple groups respectively; the linear vibration exciter groups operate synchronously; the torsional vibration exciter groups operate synchronously; the linear vibration exciter group and the torsional vibration exciter group are decoupled.

[0015] The vibration exciters of the linear vibration exciter group and the torsional vibration exciter group are both composed of eccentric rotors driven by various power sources.

[0016] The linear vibration exciter group provides axial linear vibration excitation force, and the torsional vibration exciter group provides circumferential torsional vibration excitation force. The two are respectively arranged in the vibratory hammer body, and the pile body is rigidly connected to the vibratory hammer body.

[0017] The linear vibration exciter group achieves synchronization among its various vibration exciters through a strong coupling mechanism; the torsional vibration exciter group achieves synchronization among its various vibration exciters through a strong coupling mechanism.

[0018] The excitation force for linear vibration is either low-frequency large amplitude or high-frequency small amplitude, and the excitation force for torsional vibration is either low-frequency large amplitude or high-frequency small amplitude.

[0019] The linear vibration exciter group and the torsional vibration exciter group are arranged symmetrically about the axis of the vibratory hammer and the pile, respectively.

[0020] The direction of the linear vibration excitation force is perpendicular to the plane of the torque of the torsional vibration excitation force. The plane of the torque is perpendicular to the axis of the axial direction of the vibrating hammer, and the axis of the axial direction of the vibrating hammer passes through the center point of the plane of the torque.

[0021] The linear vibration exciter group includes at least two vibration exciters, each with an eccentric rotor. When the number of vibration exciters in the linear vibration exciter group is even, the entire group is symmetrical about the axis of the vibrating hammer, the mass moments of each eccentric rotor are the same, and the phases between adjacent eccentric rotors are symmetrical about the axis of the vibrating hammer and rotate in opposite directions. When the number of vibration exciters in the linear vibration exciter group is odd, the entire group is symmetrical about the axis of the vibrating hammer, the phases between adjacent eccentric rotors are symmetrical about the axis of the vibrating hammer and rotate in opposite directions, and the sum of the mass moments of the eccentric rotors in the clockwise rotation direction is equal to the sum of the mass moments of the eccentric rotors in the counterclockwise rotation direction.

[0022] When the linear vibration exciter group has 3 vibration exciters, the eccentric rotor mass moment of the middle vibration exciter is the sum of the eccentric rotor mass moments of the vibration exciters on both sides, and the eccentric rotor mass moments of the vibration exciters on both sides are equal; the phase between adjacent eccentric rotors is symmetrical about the axial direction of the vibrating hammer and rotates in opposite directions.

[0023] The torsional vibration exciter group includes at least two torsional vibration exciters; each torsional vibration exciter is a rotating shaft with two eccentric rotors arranged on the shaft at both ends; the two eccentric rotors on each shaft have the same moment of mass and a phase difference of 180°; when the number of torsional vibration exciters is even, the eccentric rotors of each torsional vibration exciter have the same moment of mass, adjacent torsional vibration exciters rotate in opposite directions, and adjacent eccentric rotors at the same end are in the axial direction of the vibrating hammer with a phase difference of 180°; when the number of torsional vibration exciters is odd, the sum of the moment of mass of the eccentric rotors in the clockwise direction at the same end is equal to the sum of the moment of mass of the eccentric rotors in the counterclockwise direction at the same end, adjacent torsional vibration exciters rotate in opposite directions, and adjacent eccentric rotors at the same end are in the axial direction of the vibrating hammer with a phase difference of 180°.

[0024] When there are three torsional vibration exciters, the adjacent torsional vibration exciters rotate in opposite directions; the eccentric rotor mass moment of the middle torsional vibration exciter is the sum of the eccentric rotor mass moments of the torsional vibration exciters on both sides, and the eccentric rotor mass moments of the torsional vibration exciters on both sides are equal; when adjacent eccentric rotors located at the same end are in the axial direction of the vibrating hammer, the phase difference between them is 180°.

[0025] The angle between the rotation plane of the linear vibration exciter group and the plane containing the rotation axis of the torsional vibration exciter group is 0-90 degrees.

[0026] The torsional vibration exciter group includes multiple torsional vibration exciters, with the rotation centers of each exciter evenly distributed on the circumference of the same circle. The center of the gear meshing equal strong coupling mechanism is located at the center of the circle. The outer circumference of the gear meshing equal strong coupling mechanism meshes with the outer circumference of each torsional vibration exciter. The phase difference between the eccentric rotors of adjacent torsional vibration exciters is 360 / j degrees, where j is the number of torsional vibration exciters, and j≥2.

[0027] The angle between the rotation plane of the linear vibration exciter group and the plane containing the circumference of the torsional vibration exciter group is 0-90 degrees.

[0028] When the torsional vibration exciter group is set into multiple groups, the torsional vibration exciter groups are evenly distributed around the circumference of different groups; the eccentric rotors at the adjacent ends of different torsional vibration exciter groups rotate synchronously in the same direction and phase; in each torsional vibration exciter group, the shaft of one torsional vibration exciter is connected to the eccentric rotors at both ends, with a phase difference of 180°; the two eccentric rotors of the other torsional vibration exciters in the same torsional vibration exciter group are not connected, and the phase difference between them is 180°. They rotate in the opposite direction to the eccentric rotors of the adjacent torsional vibration exciter through a strong coupling mechanism, with symmetrical phases, and when the adjacent eccentric rotors at the same end are on the axis of the axial direction of the vibrating hammer, the phase difference between them is 180°; there is no intersection between the shafts of different torsional vibration exciter groups.

[0029] A method for determining the parameters of a two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer includes the following steps:

[0030] Step 1: Establish a pile-soil mechanical model;

[0031] Based on the two-dimensional dynamic driving model, the magnitudes of the vertical and torsional excitations of the vibratory hammer are calculated using the following formulas:

[0032] (1)

[0033] in, It is the excitation force for linear vibration; It is vertical static pressure; This represents the vertical harmonic load generated by the eccentric rotor. It is the excitation eccentricity of the vertical eccentric rotor. , It is the vertical excitation frequency; It is torsional torque. The circumferentially eccentric rotor generates torsional excitation. To the vertical axis of the vibratory hammer body The distance is denoted by , where i represents the direction of the resultant force generated by the left and right eccentric rotors, respectively. i=1 and i=4 represent the clockwise resultant force generated by the left and right eccentric rotors, respectively, and i=2 and i=3 represent the counterclockwise resultant force generated by the left and right eccentric rotors, respectively. It is the circumferential excitation eccentricity. , It is the torsional excitation frequency;

[0034] In vertical Direction, based on the excitation force of linear vibration This causes the vibratory hammer to vibrate up and down; in the circumferential direction Direction, through torsional excitation generated by two or more pairs of eccentric rotors. By controlling the phase angle, the centrifugal forces at the top and bottom are canceled out, causing the vibrating hammer to generate a total torsional torque. A cylindrical coordinate system is established, with the bottom of the vibratory hammer and the top of the pile connected by a fixed constraint. The motion and excitation of the vibratory hammer are transmitted through the coupling part, enabling two-dimensional dynamic drive between the pile and the vibratory hammer to achieve two types of vibration, transmitting linear vibration excitation force. and torsional moment , This represents the torsional moment transmitted at the connection between the vibratory hammer and the pile;

[0035] Step 2: Establish the preconditions for the pile-soil elastoplastic dynamics equations;

[0036] 1. Under small strain conditions, the stress-strain relationship of soil is represented by a linear elastic model;

[0037] 2. Non-cohesive soil is considered a linear elastic material;

[0038] Based on the above assumptions, the solution for a two-dimensional dynamic-driven vibratory pile driving method based on the pile-soil friction redistribution mechanism is given: the torsional moment and vertical harmonic load are generated by the vibratory hammer and act on the pile together. According to the analysis of the pile's torsional vibration force and vertical vibration force, the torsional vibration and vertical vibration of the pile are solved separately. The vertical vibration of the pile is solved using the separation of variables method based on the boundary conditions at both ends of the pile. The vertical vibration of the pile is solved using the R-K45 method. Based on the frictional interaction between the pile and the soil, the pile is subjected to a torsional excitation and a vertical excitation. The soil response is solved using the integral transform method based on the soil boundary conditions. Based on the mechanism of friction redistribution between the pile and the soil and the difference between the torsional and vertical responses between the pile and the soil, the circumferential friction force and the vertical friction force are calculated separately.

[0039] Step 3: Establish the dynamic equations for a two-dimensional, power-driven, decoupled, high-efficiency, and environmentally friendly vibratory pile hammer.

[0040] In the process of establishing the pile-soil elastoplastic dynamic equation: Under periodic load, the stress-strain relationship of the soil has two major characteristics: nonlinearity and hysteresis. The power function nonlinear dynamic model is used as the skeleton equation to reflect the nonlinear relationship of the soil under dynamic load. On this basis, according to the Masing double method, the skeleton equation is constructed into a nonlinear hysteresis curve.

[0041] When establishing the vertical drive model of a two-dimensional, dynamically driven, decoupled, high-efficiency, and environmentally friendly vibratory pile hammer, since the vibratory hammer body is directly connected to the pile, the vibratory hammer body-pile system has the same motion trajectory. Based on the dynamics of pile-soil interaction, and considering the elastoplastic properties of the soil, a cubic nonlinear hyperbolic hysteresis model of the pile's vertical motion is established, and the relationship between soil restoring force and displacement is taken as follows:

[0042] (2)

[0043] in, It is the linear elastic stiffness coefficient of the soil at the bottom of the pile. It is the maximum amplitude of the vertical displacement of the pile. It is the nonlinear coefficient of the soil reaction at the pile bottom. It is the maximum restoring force; It is a sign function, where z represents the vertical direction;

[0044] (3)

[0045] The dynamic equation for the vertical vibration of the pile is:

[0046] (4)

[0047] In equation (4), It is the total effective vibration mass. It is the vertical viscous damping coefficient of the soil. It is the vertical frictional resistance between the pile and the soil, which can be obtained from formulas (2) and (3).

[0048] (5)

[0049] , , , , , , , It is the natural frequency of the soil at the bottom of the pile. It is the damping ratio;

[0050] Substituting the introduced variables and formula (5) into formula (4), we get:

[0051] (6)

[0052] Dimensionless processing of the above equation yields the following result. , , , ;

[0053] Substituting equation (5) into equation (6), we obtain the dimensionless dynamic equation of the cubic power nonlinear hyperbolic hysteresis model of the dynamic foundation system:

[0054] (7)

[0055] in, ;

[0056] (8)

[0057] This represents the vertical relative displacement of the pile. For dimensionless restoring force, this formula is the dimensionless restoring force hyperbolic constitutive relation of the dynamic equation of the vertical vibration of the pile; the relationship between soil restoring force and displacement is modeled as a cubic power nonlinear hyperbolic hysteresis model of soil, and R-K45 is introduced to solve the nonlinear equation (7).

[0058] Due to the increased torsional vibration, there is a circumferential relative motion at the pile-soil contact surface. Based on the soil properties, there is an interaction between the soil and the vibratory hammer-pile system, resulting in circumferential frictional resistance in the pile, the magnitude of which is determined by the soil properties and depth. The equations of motion for both the vibratory hammer and the pile are established based on their respective forces and boundary conditions. Assuming the vibratory hammer is a rigid body, the circumferential differential equation for the force analysis of the vibratory hammer is as follows:

[0059] (9)

[0060] The vibratory hammer body has a solution of the following form:

[0061] (10)

[0062] It is the moment of inertia of the vibratory hammer body. From the initial state The constant that determines Depend on The constant that determines It is the undamped natural frequency. , is the natural frequency of damped vibration. It is the torsional damping coefficient between the pile and the soil. It is the torsional spring coefficient between the pile and the soil. It is the amplitude of forced vibration. , Represents phase difference;

[0063] Assuming the pile is an elastic rod, establish the torsional vibration wave equation for the pile:

[0064] (11)

[0065] The boundary conditions for the piles are:

[0066] (12)

[0067] The frictional resistance torque is generated during the interaction between the pile's exterior and interior and the soil. It is the length parameter of the pile;

[0068] The torsional vibration solution of the pile was obtained using the method of separation of variables;

[0069] (13)

[0070] in, It is the density of the pile. It is the torsional wave velocity of the pile. It is the shear modulus of the pile. It is the polar moment of inertia of the pile; by solving equation (11) using the method of separation of variables, the coefficients are obtained by solving equations (11), (12) and (13) simultaneously. Sum of coefficients ;

[0071] Formulas for the torsional moment of the pile at different locations during vibratory hammer-pile torsional vibration. as follows:

[0072] (14)

[0073] in, , It is the torsional vibration period; the shear stress at different locations of the pile is solved by calculating the torsional vibration of the pile. ;

[0074] (15)

[0075] It is the torsional section modulus of the pile;

[0076] Step 4: Establish the soil dynamics equations;

[0077] During the pile driving process, frictional resistance torque is generated by the interaction between the pile's exterior and interior and the soil. The annular section at the bottom of the pile generates a vertical harmonic excitation force on the soil. The stress wave generated by the linear vibration excitation force and the torsional moment causes the soil to move vertically and circumferentially. By performing an integral transformation on the vertical and torsional excitations using the Fourier-Bessel function, and after introducing the soil wave equation, the Green function is used to solve the soil wave equation, and the vertical, torsional and radial responses of the soil under the two excitations are obtained.

[0078] The wave equation for soil in cylindrical coordinates is established as follows:

[0079] (16)

[0080] It is the soil excitation vector. , , Representing the soil in The soil is stimulated in the direction of the excitation. The direction of the excitation, the soil in The motivation that drives the direction;

[0081]

[0082]

[0083]

[0084]

[0085]

[0086] It is the Lamé constant of soil. It is the shear modulus of soil;

[0087] A positive Fourier-Bessel transform is applied to the excitation source and the soil response;

[0088] (17) (18)

[0089] The corresponding inverse Fourier-Bessel transform is as follows;

[0090] (19)

[0091] (20)

[0092] , , , Representing the soil in Displacement response in the direction, soil in Displacement response in the direction, soil in Displacement response in the direction; It is an integral factor. It is a cylindrical coordinate axis direction, It is about The matrix, It is a Bessel function of the first kind with order n. Wavenumber It is an azimuth matrix;

[0093] In formulas (17), (18), (19) and (20),

[0094]

[0095]

[0096]

[0097] It is an indicator used to determine , , The value of needs to be determined when the load is a vertical excitation. The first row of the matrix elements and n=0, when the load is a torsional load about the vertical axis, requires the use of The second row of the matrix has element n=0; It is a Bessel function of the first kind with order n. yes First derivative;

[0098] It is a diagonal matrix; when the vertical load is about When axially symmetric, When the load is a torsional load about a vertical axis, In cylindrical coordinates, the wave equation of soil is as follows:

[0099] (twenty one)

[0100] It is the response matrix of soil;

[0101] The wave equation of soil in the frequency-wavenumber domain is shown below:

[0102] (twenty two)

[0103] , , These are the soil masses in the frequency-wavenumber domain. Response of soil in the direction, soil in the frequency-wavenumber domain Response of soil in the direction, soil in the frequency-wavenumber domain Response in direction, , , These are the soil masses in the frequency-wavenumber domain. Excitation under direction, soil in frequency-wavenumber domain Excitation under direction, soil in frequency-wavenumber domain Incentives under a specific direction;

[0104] Formula (22) is separated into two uncoupled equations, where the P-wave is a pair of coupled two-degree-of-freedom equations and the S-wave is a single-degree-of-freedom equation. The specific forms of the two equations are as follows:

[0105] (twenty three)

[0106] (twenty four)

[0107] Consider a total thickness of A homogeneous medium, with its upper surface free and its lower surface fixed, exists at a depth of... And the radius is The torsional excitation frequency at the point is The harmonic torsional load and vertical excitation frequency are The harmonic vertical load; taking the upper surface as the origin of the coordinate system, the circumferential load and vertical load are expressed as follows:

[0108] (25)

[0109] When harmonic torsional loads and harmonic vertical loads are applied to the soil, a torsional drag torque is generated. The torsional resistance torque is related to Irrelevant, and about The axis is antisymmetric; the Fourier-Bessel transforms of the harmonic torsional load and the harmonic vertical load are as follows:

[0110] (26)

[0111] Equations (23) and (24) with respect to degrees of freedom , and It is decoupled; in the frequency-wavenumber domain, the wave equation of the soil is reformulated as follows:

[0112] (27)

[0113] (28)

[0114] Horizontal wavenumber is denoted as To solve equations (27) and (28), we consider the boundary conditions and the homogeneity problem, and divide them by the shear modulus. To distinguish specific cases, the solution for the soil response is expressed as: The wave equation and boundary conditions for the soil are shown below:

[0115] (29)

[0116] , representing the P-wave velocity; Represents S-wave velocity; Represents the characteristic value of the P wave. Represents the characteristic value of the S-wave; based on the boundary conditions For soil and wave number The corresponding normal diffusion mode, Satisfying the eigenvalue equation and Based on modal superposition, the wave diffusion problem is solved and the displacement is expressed as a superposition of normal modes; the solution for the ring load is obtained according to the Hankel transform;

[0117] (30)

[0118] (31)

[0119] It refers to the depth to which the soil is stimulated. It is soil j-th order mode in the direction, It is the radius of action of the torsional excitation. It is the j-th mode of soil in the z-direction. The square of the j-th order eigenvalue of soil;

[0120] Step 5: Redistribution of frictional force at the pile-soil contact surface;

[0121] Due to the increased torsional moment, the pile generates torsional vibration. When the pile vibrates to the torsional direction, the direction of the frictional force between the pile and the soil changes. The direction of the frictional force is no longer along the axial direction of the pile, but opposite to the direction of the velocity at the micro-element on the pile surface. When the velocity and frictional force are vector-decomposed into the axial and circumferential directions of the pile, the frictional force along the axial direction of the pile is less than the total frictional force at the pile-soil contact surface, thereby reducing the axial frictional force at the pile-soil contact surface. Under the same excitation force or impact load, the penetration speed and penetration depth of the pile are increased.

[0122] The pile-soil interaction is influenced by the friction interface description, cumulative friction cycles, and elastoplastic soil response model; according to the Mohr-Coulomb criterion, the frictional resistance... It's about depth. The function is shown in the following formula:

[0123] (32)

[0124] It is the friction between the inner wall of the pile and the soil. It is the friction between the outer wall of the pile and the soil. It is the contact area between the inner wall of the pile and the soil. It is the contact area between the outer wall of the pile and the soil. It is the pile-soil interaction friction angle, It's the viscosity of the soil; It is the earth pressure coefficient. It is the effective self-weight of soil per unit;

[0125] The circumferential frictional resistance moment along the pile-soil interface is derived from the following formula:

[0126] (33)

[0127] and These are the contact area between the inner wall of the pile and the soil, and the contact area between the outer wall of the pile and the soil, respectively. It is the internal friction angle of the soil. and These are the frictional torque at the inner wall of the pile and the frictional torque at the outer wall, respectively.

[0128] The absolute velocity of the pile-soil interaction determines the distribution of frictional force between them; the pile displacement is known. Displacement of soil The speed of obtaining the pile The speed of the soil ;

[0129] The relative velocity difference between the pile and the soil is shown in the following formula:

[0130] (34)

[0131] (35)

[0132] It is the total relative velocity between the pile and the soil. Between pile and soil Relative velocity in direction, Between pile and soil Relative velocity in direction;

[0133] According to the principle of velocity vector decomposition (35), the friction force distribution law at the pile-soil friction interface is as follows:

[0134] (36)

[0135] Among them, circumferential frictional resistance axial frictional resistance ;

[0136] According to formula (36), the velocity vector determines the distribution of frictional force, and the velocity vector is determined by the ratio of the torsional vibration excitation frequency to the vertical excitation frequency. Considering the limit of shear stress that the pile can withstand, the vibration frequency ratio is selected to maximize the effect of two-dimensional dynamic driven vibratory pile driving.

[0137] The beneficial effects of this invention are: it uses a two-dimensional power source to realize the function of flexible vibration pile driving and pulling; it simultaneously performs vertical vibration and torsional vibration to meet the pile foundation depth requirements; it significantly improves the overall pile driving efficiency; it significantly reduces the cost of pile driving projects and enables effective pile driving even in hard soil conditions; it relatively reduces power consumption; the pile is not easily deformed or damaged; and the dynamic load and noise transmitted to the surrounding environment of the pile are very small. Attached Figure Description

[0138] Figure 1 This is a structural principle and dynamic model of a two-dimensional, dynamically driven, decoupled, high-efficiency, and environmentally friendly vibratory pile hammer.

[0139] Figure 2 This is a schematic diagram of the first type of two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer.

[0140] Figure 3 This is a second schematic diagram of a two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer.

[0141] Figure 4 This is a schematic diagram of the third type of two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer.

[0142] Figure 5 This is a fourth schematic diagram of a two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer.

[0143] Figure 6 This is the fifth schematic diagram of a two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer;

[0144] Figure 7 This is the sixth schematic diagram of a two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer.

[0145] Figure 8 This is the seventh schematic diagram of a two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer.

[0146] Figure 9 This is the eighth schematic diagram of a two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer.

[0147] Figure 10 This is the ninth schematic diagram of a two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer.

[0148] Figure 11 This is the tenth schematic diagram of a two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer;

[0149] Figure 12 This is the eleventh schematic diagram of a two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer.

[0150] Figure 13 This is the front view of the twelfth schematic diagram of a two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer.

[0151] Figure 14 This is a side view of the twelfth schematic diagram of a two-dimensional, power-driven, decoupled, high-efficiency, and environmentally friendly vibratory pile hammer.

[0152] Figure 15 This is a top view of the twelfth type of two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer.

[0153] Figure 16 The mechanical model of a two-dimensional dynamically driven, decoupled, high-efficiency and environmentally friendly vibratory pile hammer is shown in (a) as a front view, (b) as a top view of section AA in (a), (c) as an overall mechanical analysis, and (d) as a partial schematic diagram of the pile tip-soil contact part.

[0154] Figure 17 A calculation framework diagram for a two-dimensional, dynamically driven, decoupled, high-efficiency, and environmentally friendly vibratory pile hammer mechanical model.

[0155] Figure 18 A schematic diagram of the frictional redistribution mechanism at the pile-soil contact surface; (a) shows the application of vertical harmonic load, and (b) shows the application of both vertical and torsional harmonic loads.

[0156] Figure 19 The stress-strain relationship of the soil in cylindrical coordinates;

[0157] Figure 20 The vertical displacement and velocity of the pile;

[0158] Figure 21 Let (a) be the rotation angle and angular velocity of the vibratory hammer; (b) is the angle and (a) is the angular velocity.

[0159] Figure 22 These are the pile top rotation angle, pile bottom rotation angle, and pile body deformation angle.

[0160] Figure 23 The shear stress of the pile at different locations is shown in (a) as a three-dimensional schematic diagram and (b) as a two-dimensional schematic diagram.

[0161] Figure 24 The amplitude-frequency characteristic curve of the soil when it is excited at r=0.5m and z=2m;

[0162] Figure 25 For torsional load ( Circumferential displacement of soil at z=2m with radial r (Hz = 48Hz);

[0163] Figure 26 For vertical load ( Vertical displacement of soil at z=2m as radial r changes (24Hz);

[0164] Figure 27 For torsional load ( Circumferential displacement of soil at depth z of r=0.3m (Hz = 48Hz);

[0165] Figure 28 For vertical load ( Radial displacement of soil at depth z of r=0.3m under a 24Hz Hz surface.

[0166] Figure 29 For vertical load ( Vertical displacement of soil at depth z with r=0.3m (24Hz) as r=0.3m.

[0167] Figure 30 The ratio of vibration frequency The effect on friction distribution;

[0168] Figure 31 The ratio of vibration frequency The impact on the vertical displacement of the pile.

[0169] In the diagram: 1. Vibratory hammer body; 2. Pile body; 3. Three-machine coupled transversely arranged linear vibration exciter group; 4. Two-machine coupled vertically arranged torsional vibration exciter group; 5. Transversely arranged three-gear meshing equal-strength coupling mechanism; 6. Torsional direction two-gear meshing equal-strength coupling mechanism; 7. Vertically arranged three-gear meshing equal-strength coupling mechanism; 8. Three-machine coupled vertically arranged linear vibration exciter group; 9. Two-machine coupled linear vibration exciter group; 10. Four-machine coupled vertically arranged torsional vibration exciter group; 11. Three-machine coupled torsional vibration exciter group; 12. Four-machine coupled linear vibration exciter group; 13. Two-machine coupled transversely arranged torsional vibration exciter. Group; 14. Linear vibration two-gear meshing equal strong coupling mechanism; 15. Torsional vibration four-gear meshing equal strong coupling mechanism; 16. Four-machine coupled circular arrangement torsional vibration exciter group; 17. Torsional vibration three-gear meshing equal strong coupling mechanism; 18. Linear vibration four-gear meshing equal strong coupling mechanism; 19. Torsional vibration two-gear meshing equal strong coupling mechanism; 20. Two sets of linked torsional vibration exciter groups; 21. Torsional vibration five-gear meshing equal strong coupling mechanism; 22. Two sets of linked torsional vibration exciter groups with gear meshing equal strong coupling mechanism; 23. Two sets of linked torsional vibration exciter groups with coupling gear meshing equal strong coupling mechanism. Detailed Implementation

[0170] A two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer, such as Figure 1 As shown, the basic mechanical model structure of this two-dimensional power-driven decoupled arrangement high-efficiency and environmentally friendly vibratory pile hammer mainly includes a vibratory hammer body 1, a pile body 2, a linear vibration exciter group, and a torsional vibration exciter group; the vibration exciters in the linear vibration exciter group are synchronized through a strong coupling mechanism; the vibration exciters in the torsional vibration exciter group are synchronized through a strong coupling mechanism.

[0171] Furthermore, strong coupling mechanisms can be strong coupling mechanisms such as gear meshing, strong coupling mechanisms such as couplings, etc.

[0172] In this invention, a two-dimensional power source is provided. The two-dimensional power sources work together on the vibrating hammer 1, and the pile 2 is rigidly fixed to the vibrating hammer 1. Strong coupling mechanisms, such as couplings and gear meshing, are used to ensure the synchronous operation of the linear vibration exciter group and the torsional vibration exciter group. The two-dimensional power source acting on the vibrating hammer 1 includes a linear vibration excitation force along the axial direction of the vibrating hammer 1 and the pile 2, i.e., the first-dimensional power source F(t), and a torsional vibration excitation force around the circumferential direction of the axis of the vibrating hammer 1 and the pile 2, i.e., around the center line of the cross-section of the pile 2, as the second-dimensional power source M(t). The linear vibration exciter group generates the first-dimensional power source F(t), and the torsional vibration exciter group generates the second-dimensional power source M(t). The linear vibration excitation force along the axial direction of the vibrating hammer 1 and the pile 2 is realized by the linear vibration exciter group. The linear vibration exciter group is symmetrically arranged about the axis of the vibratory hammer 1 and the pile 2. The torsional vibration excitation force in the circumferential direction around the axis of the vibratory hammer 1 and the pile 2 is realized by the torsional vibration exciter group, which is also symmetrically arranged about the axis of the vibratory hammer 1 and the pile 2. The first-dimensional power source F(t) and the second-dimensional power source M(t) are simultaneously loaded onto the vibratory hammer 1 with the pile 2, so that the vibratory hammer 1 and the pile 2 simultaneously realize linear vibration in their axial direction and torsional vibration in the circumferential direction around their axis. This vibration mode can also be regarded as a two-dimensional dynamic composite vibration of linear vibration in the axial direction and torsional vibration in the circumferential direction around their axis, ultimately realizing the efficient and environmentally friendly vibration driving and pulling function of the vibratory pile hammer.

[0173] The vibration exciter types include eccentric rotor exciters driven by various power sources such as motors, hydraulics, pneumatics, and electromagnetics; the power driving methods of the first-dimensional power source F(t) and the second-dimensional power source M(t) can be motor-driven, electromagnetic-driven, hydraulic-driven, pneumatic-driven, etc.; motors include AC motors, DC motors, servo motors, stepper motors, etc.; hydraulic drives include hydraulic motors, hydraulic cylinders, etc.; pneumatic drives include pneumatic motors, cylinders, etc.

[0174] The linear vibration excitation force of the first-dimensional power source is perpendicular to the plane containing the torque of the torsional vibration excitation force of the second-dimensional power source, and the plane containing the torque is parallel to the radial section of the vibrating hammer 1 or the pile 2. The vibrating hammer 1 can be square, circular, or other shapes; the pile 2 can be square, circular, or other shapes. The vibration frequency and amplitude of the first-dimensional power source and the second-dimensional power source can be equal or unequal. The positions of the first-dimensional power source and the second-dimensional power source can be interchanged. Multiple linear vibration exciter groups providing the first-dimensional power source can be used, and the linkage driving linear vibration function can be achieved through a strong coupling mechanism. Multiple torsional vibration exciter groups providing the second-dimensional power source can be used, and the linkage driving torsional vibration function can be achieved through a strong coupling mechanism.

[0175] like Figure 2 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and symmetrical about the axis of the vibratory hammer 1 and the pile 2. The linear vibration exciter group has three vibratory exciters arranged laterally, forming a three-machine coupled horizontally arranged linear vibration exciter group 3. The torsional vibration exciter group has two torsional vibration exciters arranged vertically, forming a two-machine coupled vertically arranged torsional vibration exciter group 4. The vibratory exciters in the three-machine coupled horizontally arranged linear vibration exciter group 3 are synchronized through a horizontally arranged three-gear meshing equal-strength coupling mechanism 5; the torsional vibration exciters in the two-machine coupled vertically arranged torsional vibration exciter group 4 are synchronized through a torsional direction two-gear meshing equal-strength coupling mechanism 6.

[0176] The first-dimensional power source acting on the vibratory hammer 1 and the pile 2 is a linear vibration excitation force along the axial direction of the vibratory hammer 1 and the pile 2. A transversely arranged three-gear meshing, equally strong coupling mechanism 5 is used to force the eccentric rotors within each vibratory exciter in the transversely arranged three-machine coupled linear vibration exciter group 3 to operate synchronously. The transversely arranged three-machine coupled linear vibration exciter group 3 is symmetrically arranged about the axis of the vibratory hammer 1 or the pile 2. The mass moment m of the two vibratory exciters located on both sides of the transversely arranged three-machine coupled linear vibration exciter group 3 is... s r s The mass moment of the middle vibrator is equal to the sum of the mass moments of the two vibrators on either side, which is 2m. s r sThe rotation direction of the vibratory exciter located in the middle is opposite to that of the vibratory exciters located on both sides. When the three-machine coupled horizontally arranged linear vibratory exciter group 3 operates synchronously, the excitation forces of the three corresponding vibratory exciters in the direction perpendicular to the axial direction of the vibratory hammer 1 and the pile 2 cancel each other out, that is, the resultant force is 0. However, the excitation forces in the axial direction of the vibratory hammer 1 and the pile 2 are completely positively superimposed to form a linear vibration excitation force, thereby realizing the linear vibration function in the axial direction of the vibratory hammer 1 and the pile 2. The second-dimensional power source acting on the vibratory hammer 1 and the pile 2 is the torsional vibration excitation force in the circumferential direction around the axis of the vibratory hammer 1 and the pile 2. The vertically arranged torsional vibration exciter group 4 of the two machines is coupled together, including two rotating shafts and eccentric rotors arranged on the rotating shafts. Two eccentric rotors are rigidly arranged at both ends of each rotating shaft, with equal mass moments of m0r, and the phase difference between the two eccentric rotors on the same shaft is 180 degrees. The forced synchronous operation of the two vibration exciters is achieved by using a strong coupling mechanism 6 with two gears meshing in the torsional direction. When both eccentric rotors at both ends are subjected to torsional vibration... When the two gears meshing in the direction of rotation achieve synchronous rotation of the strong coupling mechanism 6, a single rotating shaft can also be used to achieve synchronous operation of the two vibration exciters. When the two machines are coupled and arranged vertically in a torsional vibration exciter group 4 operate synchronously, the excitation forces of the two vibration exciters in the axial direction of the vibrating hammer 1 and the pile 2 cancel each other out, i.e., the resultant force is 0. However, in the plane perpendicular to the axial direction of the vibrating hammer 1 and the pile 2, a torque couple of torsional vibration excitation forces with completely positive superposition around the circumferential direction of the axis of the vibrating hammer 1 and the pile 2 is formed, thereby realizing the torsional vibration function of the vibrating hammer 1 and the pile 2. The positions of the three-machine coupled horizontally arranged linear vibration exciter group 3 and the two-machine coupled vertically arranged torsional vibration exciter group 4 can be interchanged. The angle between the rotation plane of the three-machine coupled horizontally arranged linear vibration exciter group 3 and the plane where the rotating shaft of the two-machine coupled vertically arranged torsional vibration exciter group 4 is located can be 0-90 degrees.

[0177] Furthermore, multiple sets of three-machine coupled linear vibration exciter groups 3 are arranged horizontally and linked through a strong coupling mechanism to achieve the function of driving linear vibration. Alternatively, multiple sets of two-machine coupled torsional vibration exciter groups 4 are arranged vertically and linked through a strong coupling mechanism to achieve the function of driving torsional vibration.

[0178] like Figure 3 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and arranged symmetrically about the axis of the vibrating hammer 1 and the pile 2. The linear vibration exciter group is a three-machine coupled vertically arranged linear vibration exciter group 8, which has three vibration exciters arranged along the axial direction of the vibrating hammer 1 and the pile 2, with a large vibration exciter in the middle and two identical small vibration exciters at the top and bottom. The mass moment of the large vibration exciter in the middle is 2m. s r s The mass moment m of the two small vibration exciters sr s The sum of the two vibration exciters, and the rotation direction of the large vibration exciter is opposite to that of the two small vibration exciters.

[0179] The three-machine coupled vertically arranged linear vibration exciter group 8 achieves strong coupling through the vertically arranged three-gear meshing strong coupling mechanism 7. When the three-machine coupled vertically arranged linear vibration exciter group 8 operates synchronously, the excitation forces of the three corresponding vibration exciters in the direction perpendicular to the axial direction of the vibrating hammer 1 and the pile 2 cancel each other out, that is, the resultant force is 0. However, the excitation forces in the axial direction of the vibrating hammer 1 and the pile 2 are completely positively superimposed to form a linear vibration excitation force, thereby realizing the linear vibration function in the axial direction of the vibrating hammer 1 and the pile 2.

[0180] The torsional vibration exciter group 4 is a two-machine coupled vertically arranged torsional vibration exciter group 4 that achieves torsional vibration in the circumferential direction around the axis of the vibrating hammer 1 and the pile 2. The positions of the three-machine coupled vertically arranged linear vibration exciter group 8 and the two-machine coupled vertically arranged torsional vibration exciter group 4 can be interchanged. The angle between the rotation plane of the vibrating exciter of the three-machine coupled vertically arranged linear vibration exciter group 8 and the plane containing the rotation axis of the two-machine coupled vertically arranged torsional vibration exciter group 4 can be 0-90 degrees.

[0181] Furthermore, multiple sets of "three-machine coupled vertically arranged linear vibration exciter groups 8" can be used to achieve the linkage driving linear vibration function through a strong coupling mechanism. Alternatively, multiple sets of two-machine coupled vertically arranged torsional vibration exciter groups 4 can be used to achieve the linkage driving torsional vibration function through a strong coupling mechanism.

[0182] like Figure 4 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and arranged symmetrically about the axis of the vibrating hammer 1 and the pile 2. The linear vibration exciter group is a two-machine coupled linear vibration exciter group 9, comprising two vibration exciters with equal moments of mass, each m. s r sThe linear vibration exciter group 9, consisting of two coupled gears with equal strong coupling mechanism 14, ensures that the two vibrators in the two-machine coupled linear vibration exciter group 9 rotate in opposite directions. The excitation forces perpendicular to the axial direction of the vibrating hammer 1 and pile 2 cancel each other out, resulting in a net force of 0. However, the excitation forces in the axial direction of the vibrating hammer 1 and pile 2 are completely superimposed in the positive direction to form a linear vibration excitation force, thus achieving linear vibration in the axial direction of the vibrating hammer 1 and pile 2. The torsional vibration exciter group 4, consisting of two coupled vertically arranged torsional vibration exciter groups 9 and 4, achieves torsional vibration around the circumferential axis of the vibrating hammer 1 and pile 2. The positions of the two-machine coupled linear vibration exciter group 9 and the two-machine coupled vertically arranged torsional vibration exciter group 4 can be interchanged. The angle β between the rotation plane of the vibrator in the two-machine coupled linear vibration exciter group 9 and the plane containing the rotation axis of the two-machine coupled vertically arranged torsional vibration exciter group 4 is 0-90 degrees.

[0183] Furthermore, multiple sets of "two-machine coupled linear vibration exciter groups 9" can be used to achieve the linkage driving linear vibration function through a strong coupling mechanism, and multiple sets of "two-machine coupled vertically arranged torsional vibration exciter groups 4" can be used to achieve the linkage driving torsional vibration function through a strong coupling mechanism.

[0184] like Figure 5 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and arranged symmetrically about the axis of the vibrating hammer 1 and the pile 2 in the axial direction. The linear vibration exciter group is a two-machine coupled linear vibration exciter group 9. A strong coupling mechanism 14, consisting of two meshing gears, ensures that the two vibration exciters rotate in opposite directions, achieving linear vibration of the vibrating hammer 1 and the pile 2 in the axial direction.

[0185] The torsional vibration exciter group is a four-machine coupled vertically arranged torsional vibration exciter group 10, which includes four rotating shafts and eccentric rotors arranged on them. Eccentric rotors are rigidly arranged at both ends of each rotating shaft. The mass moment of each eccentric rotor is m0r, and the phase difference between two eccentric rotors on the same shaft is 180 degrees. A torsional vibration four-gear meshing strong coupling mechanism 15 is used to achieve forced synchronous operation of the different vibration exciters. When both eccentric rotors at both ends achieve synchronous rotation through the torsional vibration four-gear meshing strong coupling mechanism 15, it is also possible to use... Synchronous operation of the vibratory exciter is achieved using one, two, or three rotating shafts. When the four-machine coupled vertically arranged torsional vibratory exciter group 10 operates synchronously, the excitation forces in the axial directions of the vibratory hammer 1 and the pile 2 cancel each other out, i.e., the resultant force is 0. However, a torque couple of torsional vibration excitation forces with completely positive superposition around the circumferential direction of the axis of the vibratory hammer 1 and the pile 2 is formed in a plane perpendicular to the axial direction of the vibratory hammer 1 and the pile 2, thereby realizing the torsional vibration function around the circumferential direction of the axis of the vibratory hammer 1 and the pile 2. The positions of the two-machine coupled linear vibratory exciter group 9 and the four-machine coupled vertically arranged torsional vibratory exciter group 10 can be interchanged. The angle β between the rotation plane of the two-machine coupled linear vibratory exciter 9 and the plane containing the rotating shaft of the four-machine coupled vertically arranged torsional vibratory exciter 10 is 0-90 degrees. Multiple sets of "two-machine coupled linear vibration exciter groups" can be used to achieve the linkage driving linear vibration function through a strong coupling mechanism. Multiple sets of "four-machine coupled torsional vibration exciter groups" can be used to achieve the linkage driving torsional vibration function through a strong coupling mechanism.

[0186] like Figure 6As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and symmetrical about the axis of the vibrating hammer 1 and the pile 2 in the axial direction. The linear vibration exciter group consists of a two-machine coupled linear vibration exciter group 9, with a strong coupling mechanism 14 ensuring that the two vibration exciters rotate in opposite directions, achieving linear vibration of the vibrating hammer 1 and the pile 2 in the axial direction. The torsional vibration exciter group consists of a three-machine coupled torsional vibration exciter group 11, with strong coupling achieved through a strong coupling mechanism 17. The three-machine coupled torsional vibration exciter group 11 uses three rotating shafts. Each shaft has two eccentric rotors at both ends, with a phase difference of 180 degrees. The shafts are connected by a strong coupling mechanism such as gear meshing. The eccentric rotors at both ends of the middle shaft have a large moment of mass (2m0r), while the eccentric rotors at both ends of the upper and lower shafts have equal moments of mass (m0r). The moment of mass of the eccentric rotors at both ends of the middle shaft is the sum of the moments of the eccentric rotors at both ends of the upper and lower shafts. The three rotating shafts are parallel and arranged along the axial direction of the vibrating hammer 1 and the pile 2. The rotation direction of the vibrating exciter located on the middle shaft is the same as that of the vibrating exciter located on the two end shafts. The vibrators rotate in opposite directions. When both eccentric rotors rotate synchronously through a strong coupling mechanism 17 with a torsional vibration three-gear meshing, one or two shafts can also be used. When the three-machine coupled torsional vibration vibrator group 11 operates synchronously, the excitation forces in the axial directions of the vibrating hammer 1 and the pile 2 cancel each other out, i.e., the resultant force is 0. However, a couple of excitation forces in the circumferential direction around the axis of the vibrating hammer 1 and the pile 2 is formed in a plane perpendicular to the axial direction of the vibrating hammer 1 and the pile 2, which is completely positively superimposed. This achieves the torsional vibration function around the axis of the vibrating hammer 1 and the pile 2. The positions of the two-machine coupled linear vibration vibrator group 9 and the three-machine coupled torsional vibration vibrator group 11 can be interchanged. The angle β between the rotation plane of the two-machine coupled linear vibration vibrator group 9 and the plane containing the axis of rotation of the three-machine coupled torsional vibration vibrator group 11 is 0-90 degrees.

[0187] Furthermore, multiple sets of "two-machine coupled linear vibration exciter groups 9" can be used and the linkage driving linear vibration function can be realized through a strong coupling mechanism. Multiple sets of "three-machine coupled torsional vibration exciter groups 11" can be used and the linkage driving torsional vibration function can be realized through a strong coupling mechanism.

[0188] like Figure 7 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and arranged symmetrically about the axis of the vibrating hammer 1 and the pile 2. The linear vibration exciter group adopts a four-machine coupled linear vibration exciter group 12, and achieves strong coupling through a strong coupling mechanism 18 such as linear vibration four-gear meshing; the four-machine coupled linear vibration exciter group 12 includes four vibration exciters, each vibration exciter is equipped with an eccentric rotor, and the mass moments are respectively m s rs When all vibratory exciters operate synchronously, the excitation forces perpendicular to the axial direction of the vibratory hammer 1 and pile 2 cancel each other out, i.e., the resultant force is 0. However, the excitation forces in the axial direction of the vibratory hammer 1 and pile 2 are completely superimposed to form a linear vibration excitation force, thus achieving linear vibration in the axial direction of the vibratory hammer 1 and pile 2. The torsional vibration exciter group adopts a two-machine coupled vertical arrangement torsional vibration exciter group 4 to achieve torsional vibration in the circumferential direction around the axis of the vibratory hammer 1 and pile 2. The positions of the four-machine coupled linear vibration exciter group 12 and the two-machine coupled vertical arrangement torsional vibration exciter group 4 can be interchanged. The angle β between the rotation plane of the four-machine coupled linear vibration exciter group and the plane containing the rotation axis of the two-machine coupled vertical arrangement torsional vibration exciter group 4 is 0-90 degrees.

[0189] Furthermore, multiple sets of "four-machine coupled linear vibration exciter groups 12" can be used to achieve the linkage driving linear vibration function through a strong coupling mechanism, and multiple sets of "two-machine coupled vertically arranged torsional vibration exciter groups 4" can be used to achieve the linkage driving torsional vibration function through a strong coupling mechanism.

[0190] like Figure 8 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and symmetrical about the axis of the vibrating hammer and the pile. The linear vibration exciter group adopts a four-machine coupled linear vibration exciter group 12, and achieves strong coupling through a strong coupling mechanism 18 such as linear vibration four-gear meshing, to realize the linear vibration function of the vibrating hammer 1 and the pile 2 in the axial direction. The torsional vibration exciter group adopts a four-machine coupled vertically arranged torsional vibration exciter group 10 to realize the torsional vibration function around the axis of the vibrating hammer 1 and the pile 2 in the circumferential direction. The positions of the four-machine coupled linear vibration exciter group 12 and the four-machine coupled vertically arranged torsional vibration exciter group 10 can be interchanged.

[0191] Furthermore, the angle β between the rotation plane of the vibration exciter in the four-machine coupled linear vibration exciter group 12 and the plane containing the rotation axis of the four-machine coupled vertically arranged torsional vibration exciter group 10 is 0-90 degrees. Multiple sets of "four-machine coupled linear vibration exciter groups 12" can be used to achieve the linkage driving function of linear vibration through a strong coupling mechanism, and multiple sets of "four-machine coupled vertically arranged torsional vibration exciter groups 10" can be used to achieve the linkage driving function of torsional vibration through a strong coupling mechanism.

[0192] like Figure 9As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and symmetrical about the axis of the vibrating hammer 1 and the pile 2. The linear vibration exciter group adopts a four-machine coupled linear vibration exciter group 12, and achieves strong coupling through a linear vibration four-gear meshing strong coupling mechanism 18, realizing the linear vibration function of the vibrating hammer 1 and the pile 2 in the axial direction. The torsional vibration exciter group adopts a three-machine coupled torsional vibration exciter group 11, and achieves strong coupling through a torsional vibration three-gear meshing strong coupling mechanism 17, realizing the torsional vibration function around the axis of the vibrating hammer and the pile in the circumferential direction.

[0193] Furthermore, the positions of the four-machine coupled linear vibration exciter group 12 and the three-machine coupled torsional vibration exciter group 11 can be interchanged. The angle β between the rotation plane of the vibration exciter of the four-machine coupled linear vibration exciter group 12 and the plane containing the rotation axis of the three-machine coupled torsional vibration exciter group 11 is 0-90 degrees.

[0194] Furthermore, multiple sets of "four-machine coupled linear vibration exciter groups 12" can be used and the linkage driving linear vibration function can be realized through a strong coupling mechanism. Multiple sets of "three-machine coupled torsional vibration exciter groups 11" can be used and the linkage driving torsional vibration function can be realized through a strong coupling mechanism.

[0195] like Figure 10 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and symmetrical about the axis of the vibrating hammer 1 and the pile 2. The linear vibration exciter group consists of two coupled linear vibration exciter groups 9, with a strong coupling mechanism 14 ensuring that the two vibration exciters rotate in opposite directions, achieving linear vibration of the vibrating hammer 1 and the pile 2 in the axial direction. The torsional vibration exciter group consists of two coupled torsional vibration exciter groups 13 arranged laterally, with a strong coupling mechanism 19 ensuring strong rotation in opposite directions.

[0196] The two-machine coupled transversely arranged torsional vibration exciter group 13 includes two rotating shafts and eccentric rotors at both ends, with each eccentric rotor having a mass moment of m0r. The two eccentric rotors on the same shaft are 180 degrees out of phase, and the two rotating shafts are arranged transversely. When the two eccentric rotors on the same end but different shafts rotate to a position perpendicular to the plane containing the axis of the vibrating hammer 1 and the pile 2, the phase relationship of the two eccentric rotors on the same end is in phase, while the phase difference of the two sets of eccentric rotors on different ends is 180 degrees. When the two-machine coupled transversely arranged torsional vibration exciter group 13 operates synchronously, the excitation forces in the axial direction of the vibrating hammer 1 and the pile 2 cancel each other out, i.e., the resultant force is 0. In the plane perpendicular to the axial direction of the vibrating hammer 1 and the pile 2, a torque couple of torsional vibration excitation forces in the circumferential direction around the axis of the vibrating hammer 1 and the pile 2 is formed, which is completely positively superimposed, thereby realizing the torsional vibration function in the circumferential direction around the axis of the vibrating hammer 1 and the pile 2. The positions of the two-machine coupled linear vibration exciter group 9 and the two-machine coupled transversely arranged torsional vibration exciter group 13 can be interchanged.

[0197] Furthermore, the angle β between the rotation plane of the two-machine coupled linear vibration exciter 9 and the plane containing the rotation axis of the two-machine coupled transversely arranged torsional vibration exciter group 13 is 0-90 degrees. Multiple sets of "two-machine coupled linear vibration exciter groups 9" can be used to achieve the linkage driving function of linear vibration through a strong coupling mechanism, and multiple sets of "two-machine coupled transversely arranged torsional vibration exciter groups 13" can be used to achieve the linkage driving function of torsional vibration through a strong coupling mechanism.

[0198] like Figure 11 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and symmetrical about the axis of the vibrating hammer 1 and the pile 2. The linear vibration exciter group adopts a four-machine coupled linear vibration exciter group 12, and achieves strong coupling through a linear vibration four-gear meshing equal strong coupling mechanism 18, thereby realizing the linear vibration function of the vibrating hammer 1 and the pile 2 in the axial direction. The torsional vibration exciter group adopts a two-machine coupled transversely arranged torsional vibration exciter group 13, and achieves reverse strong coupling rotation through a torsional vibration two-gear meshing equal strong coupling mechanism 19, thereby realizing the torsional vibration function around the axis of the vibrating hammer 1 and the pile 2 in the circumferential direction. The positions of the four-machine coupled linear vibration exciter group 12 and the two-machine coupled transversely arranged torsional vibration exciter group 13 can be interchanged.

[0199] Furthermore, the angle β between the rotation plane of the four-machine coupled linear vibration exciter 12 and the plane containing the rotation axis of the two-machine coupled transversely arranged torsional vibration exciter group 13 is 0-90 degrees. Multiple sets of "four-machine coupled linear vibration exciter groups 12" can be used to achieve the linkage driving linear vibration function through a strong coupling mechanism, and multiple sets of "two-machine coupled transversely arranged torsional vibration exciter groups 13" can be used to achieve the linkage driving torsional vibration function through a strong coupling mechanism.

[0200] like Figure 12 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and arranged symmetrically about the axis of the vibrating hammer 1 and the pile 2 in the axial direction. The linear vibration exciter group adopts a four-machine coupled linear vibration exciter group 12, and achieves strong coupling through a strong coupling mechanism 18 such as linear vibration four-gear meshing, so as to realize the linear vibration function of the vibrating hammer 1 and the pile 2 in the axial direction.

[0201] The torsional vibration exciter group adopts a four-machine coupled circular arrangement torsional vibration exciter group 16. The four-machine coupled circular arrangement torsional vibration exciter group 16 includes four eccentric rotors and a torsional vibration five-gear meshing strong coupling mechanism 21 in the torsional plane. The mass moments of the four eccentric rotors are m0r respectively. The rotation plane of the four eccentric rotors is perpendicular to the axis of the vibrating hammer 1. The torsional vibration five-gear meshing strong coupling mechanism 21 is realized by the meshing of the central main gear and the eccentric rotor gears. Its axis is perpendicular to the axis of the vibrating hammer 1. The centerline of the vibratory hammer 1 coincides with that of the four eccentric rotors, which are evenly distributed around the circumference of the central main gear and rotate in the same direction, mesh with the outer circumference of the central main gear. The phase difference between any two adjacent eccentric rotors is fixed at 90 degrees. When the four-machine coupled circumferentially arranged torsional vibration exciter group 16 operates synchronously, it only generates a torque of torsional vibration excitation force in the circumferential direction around the centerlines of the vibratory hammer 1 and the pile 2, thereby realizing the torsional vibration function in the circumferential direction around the centerlines of the vibratory hammer 1 and the pile 2. The positions of the four-machine coupled linear vibration exciter group 12 and the four-machine coupled circumferentially arranged torsional vibration exciter group 16 can be interchanged.

[0202] Furthermore, multiple sets of "four-machine coupled linear vibration exciter groups 12" can be used to achieve the linkage drive linear vibration function through a strong coupling mechanism. The number of eccentric rotors in the four-machine coupled circumferentially arranged torsional vibration exciter group 16 can be expanded to j, where j≥2, and j is a natural number, thus becoming a j-machine coupled torsional vibration exciter group. The j eccentric rotors are evenly distributed on a circumferential plane perpendicular to the axis of the vibrating hammer 1 and the pile 2 and centered on the axis. Forced synchronous operation is achieved through a strong coupling mechanism such as the (j+1)th meshing gear. The phase difference between two adjacent eccentric rotors is sequentially fixed at 360 / j degrees, thereby realizing the torsional vibration function of the vibrating hammer 1 and the pile 2 driven by the "j-machine coupled torsional vibration exciter group".

[0203] like Figures 13-15 As shown, the linear vibration exciter group and the torsional vibration exciter group are decoupled and arranged symmetrically about the axis of the vibrating hammer 1 and the pile 2 in the axial direction. The linear vibration exciter group adopts a two-machine coupled linear vibration exciter group 9, which ensures that the two vibration exciters rotate in opposite directions through a strong coupling mechanism 14 of two linear vibration gears, thereby realizing the linear vibration function of the vibrating hammer 1 and the pile 2 in the axial direction; multiple groups of "two-machine coupled linear vibration exciter groups 9" can be used to realize the linkage drive linear vibration function through a strong coupling mechanism. The torsional vibration exciter group adopts two sets of linked torsional vibration exciter groups 20, that is, two sets of "two-machine coupled torsional vibration exciter groups" are driven in a linked manner. The two sets of "two-machine coupled torsional vibration exciter groups" are evenly or symmetrically arranged in a plane perpendicular to the axis of the vibrating hammer 1 and the pile 2 and centered on the axis. The two sets of linked torsional vibration exciter groups achieve synchronous operation through the gear meshing strong coupling mechanism 22 and the coupling gear meshing strong coupling mechanism 23 of the two sets of linked torsional vibration exciter groups, forming a torque of torsional vibration excitation force in the circumferential direction around the axis of the vibrating hammer 1 and the pile 2, realizing the linked drive torsional vibration function of the vibrating hammer 1 and the pile 2 in the circumferential direction around their own axis. The torsional vibration exciter group can also adopt more sets of "two sets of linked torsional vibration exciter groups 20" and achieve strong coupling linkage drive through the gear meshing strong coupling mechanism and the coupling strong coupling mechanism, thereby realizing the linked drive torsional vibration function of the vibrating hammer 1 and the pile 2. The positions of the two-machine coupled linear vibration exciter group 9 and the two-machine linked torsional vibration exciter group 20 can be interchanged. The angle between the rotation plane of the vibration exciter of the two-machine coupled linear vibration exciter group 9 and the rotation plane of the vibration exciter of the two-machine linked torsional vibration exciter group 20 is 0-90 degrees.

[0204] Example: Numerical analysis of pile-soil coupling dynamics during two-dimensional dynamically driven vibratory pile driving and pulling process;

[0205] During the simulation, the frequency corresponding to the maximum amplitude was selected as the torsional frequency based on the amplitude-frequency characteristic curve for analytical and numerical comparison; the vertical vibration frequency was selected as 24Hz; and the excitation frequency range of the soil amplitude-frequency characteristic curve was selected as 0-150Hz.

[0206] (1) Comparison of TSM (theoretical solution method) and FEM (numerical solution method) for the response of vibratory hammer-pile system;

[0207] exist Figure 20 The curves showing the vertical relative displacement and velocity of the pile, derived from RK-45, reveal that during pile penetration, the penetration rate gradually decreases as the penetration depth increases. When the penetration depth reaches a certain level, the pile stops sinking and instead vibrates in place. Figure 21 The curves in the figure show the rotation angle and angular velocity of the vibratory hammer during torsional vibration, with an angular vibration amplitude of 0.00664 rad. Figure 21 (a)), the angular velocity vibration amplitude is 2 rad / s ( Figure 21 (b)).

[0208] exist Figure 22 The curve in the figure represents the pile's response to torsional moment, with the blue and red curves representing the rotation angles at the pile top and bottom, respectively. Figure 22 It is clear from the diagram that the rotation angles of the two piles are not the same. This is because the frictional resistance torque of the soil creates a difference in rotation angle between the pile bottom and the pile top. The magenta dotted line represents the angle difference between the pile top and the pile bottom (also called torsional deformation). Figure 23 The analytical and numerical results of pile shear stress were compared. Figure 23 In (a), (z=0m), (z=2m), (z=4m), and (z=7m) represent the shear stress at different locations on the pile. The results show that the shear stress at the pile top is equal to... The shear stress at the bottom of the pile is equal to Furthermore, the shear stress gradually decreases from the pile top to the pile bottom. During the simulation, when... At that time, due to the sudden change in the pile bottom torque, stress fluctuations will occur, and these stress waves will propagate along the pile body, causing fluctuations in the simulation results. Figure 23 (b)).

[0209] (2) Comparison of TSM and FEM of soil response

[0210] The amplitude-frequency characteristics of the soil were analyzed when studying the torsional vibration frequency. Figure 24 The results are compared between the theoretical solution and the numerical simulation. The torsional vibration frequency gradually increases from 0Hz to 150Hz, and the maximum amplitude can be seen from the curve to be around 48Hz.

[0211] Calculate the effects of torsional and vertical vibrations on the soil. The frequencies of torsional and vertical vibrations are selected as follows: =48Hz and =24Hz. Figure 25 and Figure 26 These respectively demonstrate the propagation trend of the soil's vibration response along the radial coordinate under torsional and vertical vibrations. Figure 25 As can be seen, the soil response is greatest at the radius of torsional excitation. With increasing radial wavenumber, when the radial wavenumber ( When ) equals 1, the torsional response of the soil has decayed to zero. Figure 26The vertical displacement response curve of the soil under vertical excitation can be seen, and the soil response is maximum at the excitation radius. As the radial wavenumber increases, the vertical response of the soil oscillates and decays with increasing radial wavenumber. When the radial wavenumber ( When the value is 8, the torsional response can be ignored.

[0212] exist Figure 27 Tables 28 and 29 show the soil response at different depths under torsional and vertical vibrations. Figure 27-29 In the middle, when the load is applied at a depth m and radius At position m, the soil response at the applied load is the largest, and the soil response decays rapidly with increasing distance from the vibration source on the vertical coordinate. Figure 29 In the middle, since the ground surface (z=0m) is in a free state, the soil will be affected by stress waves in this state and the displacement will be non-zero. At a depth of z=4m (fixed constraint), the soil response will gradually decay to zero.

[0213] (3) Vibration frequency ratio The impact;

[0214] This study investigates the influence of torsional vibration frequency and vertical vibration frequency on the distribution of frictional force. Based on... Figure 30 As shown, when (torsional vibration frequency) =0Hz, vertical frequency At Hz = 24Hz, the vertical frictional force between the pile and the soil is equal to the total frictional force of 11676N (red dashed line); when (torsion frequency is) =24Hz, vertical frequency At 24Hz, the vertical friction force is 8256N (blue dashed line), and the circumferential friction force is 8256N (blue solid line); when (torsion frequency is) =48Hz, vertical frequency At 24Hz, the vertical friction force is 5222N (magenta dashed line), and the circumferential friction force is 104400N (magenta solid line). During pile driving, vertical friction force (pile driving resistance) is the cause of impediment to pile driving, while circumferential friction resistance has no impeding effect on pile driving. Figure 30 The calculation results show that as the frequency ratio increases, the vertical friction decreases while the circumferential friction increases.

[0215] Based on the frictional redistribution mechanism, comparisons were made. , and The ratio of the three vibration frequencies The calculation results under the given circumstances. From Figure 31As can be seen from this, when the penetration depth At that time, there were three points. (62.95s, 2m) (49.73s, 2m) and (42.98s, 2m), the pile driving time decreases with increasing vibration frequency ratio. When the pile driving time t=150s, corresponding to three points... (150s, 2.643m) (150s, 3.469m) and (150s, 4.616m) The pile penetration depth increases with the increase of the vibration frequency ratio. The comparison of the calculation results verifies that the friction redistribution mechanism is effective, and increasing torsional vibration can improve the pile penetration speed and depth.

Claims

1. A two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer, characterized in that, It includes a linear vibration exciter group and a torsional vibration exciter group; the linear vibration exciter group and the torsional vibration exciter group are arranged in one or more groups respectively; the linear vibration exciter groups operate synchronously; the torsional vibration exciter groups operate synchronously; the linear vibration exciter group and the torsional vibration exciter group are decoupled from each other. The vibration exciters of the linear vibration exciter group and the torsional vibration exciter group are both composed of eccentric rotors driven by various power sources. The linear vibration exciter group provides axial linear vibration excitation force, and the torsional vibration exciter group provides circumferential torsional vibration excitation force. The two are respectively arranged in the vibrating hammer body (1), and the pile body (2) is rigidly connected to the vibrating hammer body (1). The linear vibration exciter group achieves synchronization among the vibration exciters through a strong coupling mechanism; the torsional vibration exciter group achieves synchronization among the vibration exciters through a strong coupling mechanism.

2. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 1, characterized in that, The excitation force for linear vibration is either low-frequency large amplitude or high-frequency small amplitude, and the excitation force for torsional vibration is either low-frequency large amplitude or high-frequency small amplitude.

3. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 1, characterized in that, The linear vibration exciter group and the torsional vibration exciter group are arranged symmetrically about the axis of the vibrating hammer (1) and the pile (2), respectively.

4. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 1, characterized in that, The direction of the linear vibration excitation force is perpendicular to the plane of the torque of the torsional vibration excitation force. The plane of the torque is perpendicular to the axis of the axial direction of the vibrating hammer (1), and the axis of the axial direction of the vibrating hammer (1) passes through the center point of the plane of the torque.

5. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 1, characterized in that, The linear vibration exciter group includes at least two vibration exciters, each of which is equipped with an eccentric rotor. When the number of vibration exciters in the linear vibration exciter group is even, the whole is symmetrical about the axis of the vibration hammer (1) in the axial direction, each eccentric rotor has the same mass moment, and the phase between each adjacent eccentric rotor is symmetrical about the axis of the vibration hammer (1) and rotates in the opposite direction. When the number of vibration exciters in the linear vibration exciter group is odd, the whole is symmetrical about the axis of the vibration hammer (1) in the axial direction, each adjacent eccentric rotor has the same phase about the axis of the vibration hammer (1) and rotates in the opposite direction, and the sum of the mass moments of the eccentric rotors in the clockwise rotation direction is equal to the sum of the mass moments of the eccentric rotors in the counterclockwise rotation direction.

6. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 5, characterized in that, When the number of vibration exciters in the linear vibration exciter group is 3, the eccentric rotor mass moment of the middle vibration exciter is the sum of the eccentric rotor mass moments of the vibration exciters on both sides, and the eccentric rotor mass moments of the vibration exciters on both sides are equal; the phase between adjacent eccentric rotors is symmetrical about the axial direction of the vibration hammer (1), and they rotate in opposite directions.

7. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 1, characterized in that, The torsional vibration exciter group includes at least two torsional vibration exciters; each torsional vibration exciter is a rotating shaft with two eccentric rotors arranged on it, and the two eccentric rotors are located at the two ends of the rotating shaft respectively; the two eccentric rotors on each rotating shaft have the same mass moment and a phase difference of 180°; when the number of torsional vibration exciters is even, the eccentric rotors of each torsional vibration exciter have the same mass moment, the adjacent torsional vibration exciters rotate in opposite directions, and the adjacent eccentric rotors at the same end are in the axial direction of the vibrating hammer (1) with a phase difference of 180°; when the number of torsional vibration exciters is odd, the sum of the mass moments of the eccentric rotors in the clockwise rotation direction at the same end is equal to the sum of the mass moments of the eccentric rotors in the counterclockwise rotation direction at the same end, the adjacent torsional vibration exciters rotate in opposite directions, and the adjacent eccentric rotors at the same end are in the axial direction of the vibrating hammer (1) with a phase difference of 180°.

8. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 7, characterized in that, When there are three torsional vibration exciters in the torsional vibration exciter group, the adjacent torsional vibration exciters rotate in opposite directions; the eccentric rotor mass moment of the middle torsional vibration exciter is the sum of the eccentric rotor mass moments of the torsional vibration exciters on both sides, and the eccentric rotor mass moments of the torsional vibration exciters on both sides are equal; when the adjacent eccentric rotors located at the same end are in the axial direction of the vibrating hammer (1), the phase difference between them is 180°.

9. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 7 or 8, characterized in that, The angle between the rotation plane of the linear vibration exciter group and the plane containing the rotation axis of the torsional vibration exciter group is 0-90 degrees.

10. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 1, characterized in that, The torsional vibration exciter group includes multiple torsional vibration exciters, with the rotation centers of each exciter evenly distributed on the circumference of the same circle. The center of the gear meshing equal strong coupling mechanism is located at the center of the circle. The outer circumference of the gear meshing equal strong coupling mechanism meshes with the outer circumference of each torsional vibration exciter. The phase difference between the eccentric rotors of adjacent torsional vibration exciters is 360 / j degrees, where j is the number of torsional vibration exciters, and j≥2.

11. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 10, characterized in that, The angle between the rotation plane of the linear vibration exciter group and the plane containing the circumference of the torsional vibration exciter group is 0-90 degrees.

12. The two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer according to claim 7, characterized in that, When the torsional vibration exciter group is set into multiple groups, the torsional vibration exciter groups of different groups are evenly distributed around the circumference; the adjacent eccentric rotors of different torsional vibration exciter groups rotate synchronously in the same direction and phase; in each torsional vibration exciter group, the shaft of one torsional vibration exciter is connected to the eccentric rotors at both ends, with a phase difference of 180°; the two eccentric rotors of the other torsional vibration exciter groups in the same group are not connected, with a phase difference of 180°, and rotate in the opposite direction to the eccentric rotors of the adjacent torsional vibration exciter through a strong coupling mechanism, with symmetrical phases, and the adjacent eccentric rotors located at the same end have a phase difference of 180° when they are in the axial direction of the vibration hammer body (1); there is no intersection between the shafts of different torsional vibration exciter groups.

13. A method for determining the parameters of a two-dimensional power-driven decoupled high-efficiency and environmentally friendly vibratory pile hammer as described in any one of claims 1-12, characterized in that, Includes the following steps: Step 1: Establish a pile-soil mechanical model; Based on the two-dimensional dynamic driving model, the magnitudes of the vertical and torsional excitations of the vibratory hammer are calculated using the following formulas: (1) ； in, It is the excitation force for linear vibration; It is vertical static pressure; This represents the vertical harmonic load generated by the eccentric rotor. It is the excitation eccentricity of the vertical eccentric rotor. , It is the vertical excitation frequency; It is torsional torque. The circumferentially eccentric rotor generates torsional excitation. To the vertical axis of the vibratory hammer body The distance is denoted by , where i represents the direction of the resultant force generated by the left and right eccentric rotors, respectively. i=1 and i=4 represent the clockwise resultant force generated by the left and right eccentric rotors, respectively, and i=2 and i=3 represent the counterclockwise resultant force generated by the left and right eccentric rotors, respectively. It is the circumferential excitation eccentricity. , It is the torsional excitation frequency; In vertical Direction, based on the excitation force of linear vibration This causes the vibrating hammer to vibrate up and down; in the circumferential direction Direction, through torsional excitation generated by multiple pairs of eccentric rotors. By controlling the phase angle, the centrifugal forces at the top and bottom are canceled out, causing the vibrating hammer to generate a total torsional torque. A cylindrical coordinate system is established, with the bottom of the vibratory hammer and the top of the pile connected by a fixed constraint. The motion and excitation of the vibratory hammer are transmitted through the coupling part, enabling two-dimensional dynamic drive between the pile and the vibratory hammer to achieve two types of vibration, transmitting linear vibration excitation force. and torsional moment , This represents the torsional moment transmitted at the connection between the vibratory hammer and the pile; Step 2: Establish the preconditions for the pile-soil elastoplastic dynamics equations; 1) Under small strain conditions, the stress-strain relationship of soil is represented by a linear elastic model; 2) Non-cohesive soil is considered a linear elastic material; Based on the above assumptions, the solution for a two-dimensional dynamic-driven vibratory pile driving method based on the pile-soil friction redistribution mechanism is given: the torsional moment and vertical harmonic load generated by the vibratory hammer act together on the pile. Based on the analysis of the pile's torsional and vertical vibration forces, the torsional and vertical vibrations of the pile are solved separately. The vertical vibration of the pile is solved using the separation of variables method based on the boundary conditions at both ends of the pile, and the vertical vibration of the pile is solved using the R-K45 method. Based on the frictional interaction between the pile and soil, the pile provides the soil with both torsional and vertical excitations. The soil response is solved using the integral transform method based on the soil's boundary conditions. Based on the mechanism of friction redistribution between the pile and soil and the difference between the torsional and vertical responses between the pile and soil, the circumferential friction force and the vertical friction force are calculated separately. Step 3: Establish the dynamic equations for a two-dimensional, power-driven, decoupled, high-efficiency, and environmentally friendly vibratory pile hammer. In the process of establishing the pile-soil elastoplastic dynamic equation: Under periodic load, the stress-strain relationship of the soil has two major characteristics: nonlinearity and hysteresis. The power function nonlinear dynamic model is used as the skeleton equation to reflect the nonlinear relationship of the soil under dynamic load. On this basis, according to the Masing double method, the skeleton equation is constructed into a nonlinear hysteresis curve. When establishing the vertical drive model of a two-dimensional, dynamically driven, decoupled, high-efficiency, and environmentally friendly vibratory pile hammer, since the vibratory hammer body is directly connected to the pile, the vibratory hammer body-pile system has the same motion trajectory. Based on the dynamics of pile-soil interaction, and considering the elastoplastic properties of the soil, a cubic nonlinear hyperbolic hysteresis model of the pile's vertical motion is established, and the relationship between soil restoring force and displacement is taken as follows: (2) ； in, It is the linear elastic stiffness coefficient of the soil at the bottom of the pile. It is the maximum amplitude of the vertical displacement of the pile. It is the nonlinear coefficient of the soil reaction at the pile bottom. It is the maximum restoring force; It is a sign function, where z represents the vertical direction; (3) ； The dynamic equation for the vertical vibration of the pile is: (4) ； In equation (4), It is the total effective vibration mass. It is the vertical viscous damping coefficient of the soil. It is the vertical frictional resistance between the pile and the soil, which can be obtained from formulas (2) and (3). (5) ； , , , , , , , It is the natural frequency of the soil at the bottom of the pile. It is the damping ratio; Substituting the introduced variables and formula (5) into formula (4), we get: (6) ； Dimensionless processing of the above equation yields the following result. , , , ; Substituting equation (5) into equation (6), we obtain the dimensionless dynamic equation of the cubic power nonlinear hyperbolic hysteresis model of the dynamic foundation system: (7) ； in, ; (8) ； This represents the vertical relative displacement of the pile. For dimensionless restoring force, this formula is the dimensionless restoring force hyperbolic constitutive relation of the dynamic equation of the vertical vibration of the pile; the relationship between soil restoring force and displacement is modeled as a cubic power nonlinear hyperbolic hysteresis model of soil, and R-K45 is introduced to solve the nonlinear equation (7). Due to the increased torsional vibration, there is a circumferential relative motion at the pile-soil contact surface. Based on the soil properties, there is an interaction between the soil and the vibratory hammer-pile system, resulting in circumferential frictional resistance in the pile, the magnitude of which is determined by the soil properties and depth. The equations of motion for both the vibratory hammer and the pile are established based on their respective forces and boundary conditions. Assuming the vibratory hammer is a rigid body, the circumferential differential equation for the force analysis of the vibratory hammer is as follows: (9) ； The vibratory hammer body has a solution of the following form: (10) ； It is the moment of inertia of the vibratory hammer body. From the initial state The constant that determines Depend on The constant that determines It is the undamped natural frequency. , is the natural frequency of damped vibration. It is the torsional damping coefficient between the pile and the soil. It is the torsional spring coefficient between the pile and the soil. It is the amplitude of forced vibration. , Represents phase difference; Assuming the pile is an elastic rod, establish the torsional vibration wave equation for the pile: (11) ； The boundary conditions for the piles are: (12) ； The frictional resistance torque is generated during the interaction between the pile's exterior and interior and the soil. It is the length parameter of the pile; The torsional vibration solution of the pile was obtained using the method of separation of variables; (13) ； in, It is the density of the pile. It is the torsional wave velocity of the pile. It is the shear modulus of the pile. It is the polar moment of inertia of the pile; by solving equation (11) using the method of separation of variables, the coefficients are obtained by solving equations (11), (12) and (13) simultaneously. Sum of coefficients ; Formulas for the torsional moment of the pile at different locations during vibratory hammer-pile torsional vibration. as follows: (14) ； in, , It is the torsional vibration period; the shear stress at different locations of the pile is solved by calculating the torsional vibration of the pile. ; (15) ； It is the torsional section modulus of the pile; Step 4: Establish the soil dynamics equations; During the pile driving process, frictional resistance torque is generated by the interaction between the pile's exterior and interior and the soil. The annular section at the bottom of the pile generates a vertical harmonic excitation force on the soil. The stress wave generated by the linear vibration excitation force and the torsional moment causes the soil to move vertically and circumferentially. By performing an integral transformation on the vertical and torsional excitations using the Fourier-Bessel function, and after introducing the soil wave equation, the Green function is used to solve the soil wave equation, and the vertical, torsional and radial responses of the soil under the two excitations are obtained. The wave equation for soil in cylindrical coordinates is established in the following form: (16) ； It is the soil excitation vector. , , Representing the soil in The direction of the excitation, the soil in The direction of the excitation, the soil in The motivation that drives the direction; ； ； ； ； ； It is the Lamé constant of soil. It is the shear modulus of soil; A positive Fourier-Bessel transform is applied to the excitation source and the soil response; (17) ； (18) ； The corresponding inverse Fourier-Bessel transform is as follows; (19) ； (20) ； , , , Representing the soil in Displacement response in the direction, soil in Displacement response in the direction, soil in Displacement response in the direction; It is an integral factor. It is a cylindrical coordinate axis direction, It is about The matrix, It is a Bessel function of the first kind with order n. It is wave number, It is an azimuth matrix; In formulas (17), (18), (19) and (20), ； ； ； It is an indicator used to determine , , The value of needs to be used when the load is a vertical excitation. The first row of the matrix elements and n=0, when the load is a torsional load about the vertical axis, requires the use of The second row of the matrix elements and n=0; It is a Bessel function of the first kind with order n. yes First derivative; It is a diagonal matrix; when the vertical load is about When axially symmetric, When the load is a torsional load about a vertical axis, In cylindrical coordinates, the wave equation of soil is as follows: (21) ； It is the response matrix of soil; The wave equation of soil in the frequency-wavenumber domain is shown below: (22) ； , , These are the soil masses in the frequency-wavenumber domain. Response of soil in the direction, soil in the frequency-wavenumber domain Response of soil in the direction, soil in the frequency-wavenumber domain Response in direction, , , These are the soil masses in the frequency-wavenumber domain. Excitation under direction, soil in frequency-wavenumber domain Excitation under direction, soil in frequency-wavenumber domain Incentives under a specific direction; Formula (22) is separated into two uncoupled equations, where the P-wave is a pair of coupled two-degree-of-freedom equations and the S-wave is a single-degree-of-freedom equation. The specific forms of the two equations are as follows: (23) ； (24) ； Consider a total thickness of A homogeneous medium, with its upper surface free and its lower surface fixed, exists at a depth of... And the radius is The torsional excitation frequency at the point is The harmonic torsional load and vertical excitation frequency are The harmonic vertical load; taking the upper surface as the origin of the coordinate system, the circumferential load and vertical load are expressed as follows: (25) ； When harmonic torsional loads and harmonic vertical loads are applied to the soil, a torsional drag torque is generated. The torsional resistance torque is related to Irrelevant, and about The axis is antisymmetric; the Fourier-Bessel transforms of the harmonic torsional load and the harmonic vertical load are as follows: (26) ； Equations (23) and (24) with respect to degrees of freedom , and It is decoupled; in the frequency-wavenumber domain, the wave equation of the soil is reformulated as follows: (27) ； (28) ； Horizontal wavenumber is denoted as To solve equations (27) and (28), we consider the boundary conditions and the homogeneity problem, and divide them by the shear modulus. To distinguish specific cases, the solution for the soil response is expressed as: The wave equation and boundary conditions for the soil are shown below: (29) ； , representing the P-wave velocity; Represents S-wave velocity; Represents the characteristic value of the P wave. Represents the characteristic value of the S-wave; based on the boundary conditions For soil and wavenumber The corresponding normal diffusion mode, Satisfying the eigenvalue equation and Based on modal superposition, the wave diffusion problem is solved and the displacement is expressed as a superposition of normal modes; the solution for the ring load is obtained according to the Hankel transform; (30) ； (31) ； It refers to the depth to which the soil is stimulated. It is soil j-th order mode in the direction, It is the radius of action of the torsional excitation. It is the j-th mode of soil in the z-direction. It is the square of the j-th order eigenvalue of the soil; Step 5: Redistribution of frictional force at the pile-soil contact surface; Due to the increased torsional moment, the pile generates torsional vibration. When the pile vibrates to the torsional direction, the direction of the frictional force between the pile and the soil changes. The direction of the frictional force is no longer along the axial direction of the pile, but opposite to the direction of the velocity at the micro-element on the pile surface. When the velocity and frictional force are vector-decomposed into the axial and circumferential directions of the pile, the frictional force along the axial direction of the pile is less than the total frictional force at the pile-soil contact surface, thereby reducing the axial frictional force at the pile-soil contact surface. Under the same excitation force or impact load, the penetration speed and penetration depth of the pile are increased. The pile-soil interaction is influenced by the friction interface description, cumulative friction cycles, and elastoplastic soil response model; according to the Mohr-Coulomb criterion, the frictional resistance... It's about depth. The function is shown in the following formula: (32) ； It is the friction between the inner wall of the pile and the soil. It is the friction between the outer wall of the pile and the soil. It is the contact area between the inner wall of the pile and the soil. It is the contact area between the outer wall of the pile and the soil. It is the pile-soil interaction friction angle, It's the viscosity of the soil; It is the earth pressure coefficient. It is the effective self-weight of soil per unit; The circumferential frictional resistance moment along the pile-soil interface is derived from the following formula: (33) ； and These are the contact area between the inner wall of the pile and the soil, and the contact area between the outer wall of the pile and the soil, respectively. It is the internal friction angle of the soil. and These are the frictional torque at the inner wall of the pile and the frictional torque at the outer wall, respectively. The absolute velocity of the pile-soil interaction determines the distribution of frictional force between them; the pile displacement is known. Displacement of soil The speed of obtaining the pile The speed of the soil ; The relative velocity difference between the pile and the soil is shown in the following formula: (34) ； (35) ； It is the total relative velocity between the pile and the soil. Between pile and soil Relative velocity in direction, Between pile and soil Relative velocity in the direction; According to the principle of velocity vector decomposition (35), the friction force distribution law at the pile-soil friction interface is as follows: (36) ； Among them, circumferential frictional resistance axial frictional resistance ; According to formula (36), the velocity vector determines the distribution of frictional force, and the velocity vector is determined by the ratio of the torsional excitation frequency to the vertical excitation frequency. Considering the limit of shear stress that the pile can withstand, the vibration frequency ratio is selected to maximize the effect of two-dimensional dynamic driven vibratory pile driving.

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