Axial plunger pump active vibration reduction method and device based on magnetic force reverse excitation

Abstract

The invention discloses an axial plunger pump active vibration reduction method and device based on magnetic force reverse excitation. The method comprises the steps that S1, vibration information of a plunger pump and a swash plate is collected in real time; s2, the controller extracts pulsation parameters of the vibration information, then predicts pulsation parameters at the next moment based on the real-time pulsation parameters through a prediction model, obtains corresponding excitation force according to the pulsation parameters, and calculates target force needed for counteracting the excitation force at the next moment; s3, the controller controls the current flowing through the coil assembly based on the target force to enable the coil assembly to generate a first magnetic field; the permanent magnet assembly in the sliding shoe generates a second magnetic field, the first magnetic field and the second magnetic field interact to generate counter-acting force for counteracting the exciting force, and alternating exciting force caused by pressure pulsation of the plunger cavity is restrained in real time.

Description

Technical Field

[0001] This invention relates to the field of hydraulic pump vibration reduction technology, and in particular to an active vibration reduction method and device for axial piston pumps based on magnetic reverse excitation. Background Technology

[0002] As the core power component of a hydraulic system, the axial piston pump experiences vibrations induced by periodic pressure pulsations in the piston chamber, reciprocating inertial impacts of the piston assembly, and dynamic load variations in the slipper-swashplate pair. These vibrations represent a key technological bottleneck hindering its development towards higher pressure, higher speed, higher reliability, and lower noise. In particular, the slipper-swashplate friction pair, as the critical interface for transmitting hydraulic pulsating loads, directly impacts the pump's mechanical efficiency, component lifespan, and system noise radiation.

[0003] Existing vibration reduction technologies mostly focus on structural optimization, the application of passive damping materials, or global vibration isolation. These methods are effective for low- and medium-frequency vibrations, but their ability to suppress high-frequency vibrations caused by forced vibrations in the slipper is limited, and they are difficult to adapt to varying operating conditions. Therefore, there is an urgent need for an active vibration reduction solution that does not interfere with the core lubrication and load-bearing functions of the slipper bottom, can accurately sense and counteract high-frequency hydraulic excitation forces in real time, and has adaptive and predictive capabilities, in order to improve the operational stability of the slipper pair from the source. Summary of the Invention

[0004] This invention provides an active vibration reduction method and device for an axial piston pump based on magnetic reverse excitation, which aims to suppress high-frequency vibration of the slipper by introducing magnetic force as an active control force.

[0005] To achieve the above objectives, the present invention provides the following technical solution:

[0006] An active vibration reduction method for an axial piston pump based on magnetic reverse excitation includes:

[0007] S1. Real-time acquisition of vibration information, including pressure pulsation data at the outlet of the plunger pump and vibration signals transmitted to the swashplate;

[0008] S2. The controller extracts the pulsation parameters of the vibration information, then predicts the pulsation parameters at the next moment based on the real-time pulsation parameters using a prediction model, and then calculates the target force required to counteract the excitation force at the next moment.

[0009] S3. The controller controls the current flowing through the coil assembly based on the target force, so that it generates a first magnetic field; the permanent magnet assembly in the slipper generates a second magnetic field, and the coil assembly is set in the swashplate. Through the interaction of the first magnetic field and the second magnetic field, a reaction force is generated to counteract the excitation force and suppress the vibration of the slipper.

[0010] Furthermore, the target force and the excitation force are equal in magnitude and opposite in direction. In step S3, the controller, in conjunction with an active waveform cancellation algorithm, generates a drive current signal corresponding to the drive current, and adjusts the generation direction and magnitude of the first magnetic field in real time.

[0011] Furthermore, the controller can also calculate the propagation delay τ of the pressure wave from the acquisition location of the vibration message to the slipper, and perform phase correction on the output phase of the drive current signal.

[0012] Furthermore, the driving current is ,in, The effective magnetic circuit length of the coil assembly is... The total number of turns of the annular electromagnetic coil within the coil assembly. The permeability of free space, The force-to-magnetic field conversion coefficient, For the overall force transmission coefficient, This refers to the equivalent working area of ​​the plunger pump. The predicted instantaneous pressure pulsation value at the outlet of the plunger pump. .

[0013] Furthermore, it also includes step S4: the controller records the actual vibration message after the reaction force compensation in step S3 at the next moment, and adaptively adjusts the parameters of the prediction model.

[0014] An active vibration damping device for an axial piston pump based on magnetic reverse excitation, capable of achieving the method described above, includes a slipper and a swashplate. The swashplate is equipped with a coil assembly at a position corresponding to the oil discharge area of ​​the piston pump, and the slipper is equipped with a permanent magnet assembly. It also includes a detection assembly for collecting vibration messages and transmitting them to a controller. The controller signal is connected to the coil assembly to receive the vibration messages and generate the driving current, thereby controlling the direction and magnitude of the first magnetic field in real time to achieve vibration damping.

[0015] Furthermore, the controller includes a phase-locking module, an amplitude matching module, and a phase delay compensation module connected by signals, which can extract the pulsation parameters, including the dominant vibration frequency, real-time phase, amplitude, and vibration acceleration characteristics, based on the vibration information; it also includes a digital signal processor, which has the machine learning model built in it, and can predict future pulsation trends based on the pulsation parameters.

[0016] Furthermore, the head of the slipper is provided with a plurality of first mounting grooves along its axial direction for mounting the permanent magnet assembly. Each of the first mounting grooves is distributed in a variable diameter spiral shape. The permanent magnet assembly includes a plurality of magnetic block units, and the distribution radius of each magnetic block unit increases in the direction close to the plunger pump.

[0017] Furthermore, the swash plate is provided with a second mounting groove corresponding to the coil assembly in the oil discharge area of ​​the plunger pump, and the second mounting groove is fan-shaped.

[0018] Furthermore, the inclined plate is also provided with an annular cooling channel, which can be connected to a fan.

[0019] The beneficial effects of this invention are:

[0020] 1. The present invention proposes an active vibration reduction method for an axial piston pump based on magnetic reverse excitation, comprising the following steps: S1, real-time acquisition of vibration information at the piston pump and swashplate; S2, the controller extracts the pulsation parameters of the vibration information, and then predicts the pulsation parameters at the next moment based on the real-time pulsation parameters through a prediction model, obtains the corresponding excitation force from the pulsation parameters, and calculates the target force required to counteract the excitation force at the next moment; S3, the controller controls the current flowing through the coil assembly based on the target force to generate a first magnetic field; the permanent magnet assembly in the slipper generates a second magnetic field, and the interaction between the first magnetic field and the second magnetic field generates a reaction force to counteract the excitation force, thereby suppressing the alternating excitation force caused by the pressure pulsation in the piston cavity in real time.

[0021] 2. The present invention proposes an active vibration reduction method for an axial piston pump based on magnetic reverse excitation. The controller can also calculate the propagation delay time τ of the pressure wave from the vibration message acquisition location to the slipper, and perform phase correction on the output phase of the drive current signal, effectively avoiding the force cancellation phase deviation caused by the propagation delay, and improving the real-time performance and accuracy of the vibration reduction effect.

[0022] 3. The present invention proposes an active vibration reduction method for an axial piston pump based on magnetic reverse excitation, which further includes step S4: the controller records the actual vibration message after the reaction force compensation at the next moment, and adaptively adjusts the prediction model so that the prediction model can continuously adapt to the changes in the current operating conditions of the piston pump, further improve the accuracy of the excitation force prediction at future moments, ensure the real-time performance and accuracy of the reaction force, and thus achieve a long-term stable active vibration reduction effect.

[0023] 4. This invention proposes an active vibration damping device for an axial piston pump based on magnetic reverse excitation. The controller includes a phase-locking module, an amplitude matching module, and a phase delay compensation module for signal connections. By dynamically adjusting the output phase of the drive current signal, it ensures that the extracted real-time phase remains synchronized with the actual vibration state, thereby effectively eliminating phase deviation caused by pressure wave propagation delay. It also includes a digital signal processor with a built-in machine learning model capable of predicting future pressure pulsation trends.

[0024] 5. This invention proposes an active vibration damping device for an axial piston pump based on magnetic reverse excitation, comprising a swashplate and a slipper. The head of the slipper is provided with several first mounting grooves arranged in a variable-diameter spiral pattern along its axial direction. The design of the first mounting grooves adapts to the shape of the slipper, avoiding damage to the hydrostatic support structure at the bottom of the slipper. The first mounting grooves are used to install permanent magnet components, which include several magnetic block units, with the distribution radius of each magnetic block unit increasing towards the piston pump.

[0025] 6. The present invention proposes an active vibration damping device for an axial piston pump based on magnetic reverse excitation. The swashplate is also provided with an annular cooling channel, which can be connected to a fan to ensure that the working temperature of the coil assembly is controlled within a set threshold range, and to avoid the change in coil resistance due to excessive temperature affecting the stability of the magnetic field strength. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of the invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] Figure 1 This is a schematic diagram of an active vibration reduction method for an axial piston pump based on magnetic reverse excitation according to the present invention;

[0028] Figure 2 This is a schematic diagram of a swashplate for an axial piston pump active vibration damping device based on magnetic reverse excitation according to the present invention.

[0029] Figure 3 for Figure 2 A cross-sectional view along the AA direction;

[0030] Figure 4 This is a schematic diagram of a slipper for an axial piston pump active vibration damping device based on magnetic reverse excitation according to the present invention;

[0031] Figure 5 for Figure 4 A sectional view along the BB direction;

[0032] Figure 6 This is a flowchart of an active vibration reduction method for an axial piston pump based on magnetic reverse excitation according to the present invention;

[0033] In the diagram, 1 is the slipper; 2 is the permanent magnet assembly; 3 is the swashplate; 4 is the coil assembly; 5 is the high-frequency pressure pulsation sensor; 6 is the controller; 7 is the vibration acceleration sensor; and 8 is the distribution plate. Detailed Implementation

[0034] The following is combined Figure 1-6 The present invention will be described in detail below.

[0035] Example 1

[0036] This embodiment provides an active vibration reduction method for an axial piston pump based on magnetic reverse excitation, including:

[0037] S1. Real-time acquisition of vibration information, including pressure pulsation data at the piston pump outlet and vibration signals transmitted to swashplate 3;

[0038] S2 and controller 6 extract multimodal pulsation parameters of vibration information, and then predict the pulsation parameters at the next moment based on the real-time pulsation parameters through the prediction model, and calculate the target force required to counteract the excitation force at the next moment.

[0039] S3, the controller 6 controls the current flowing through the coil assembly 4 based on the target force, so that it generates a first magnetic field; the permanent magnet assembly 2 in the slipper 1 generates a second magnetic field, and the coil assembly 4 is set in the swashplate 3. Through the interaction of the first magnetic field and the second magnetic field, a reaction force is generated to counteract the excitation force and suppress the vibration of the slipper 1.

[0040] In this embodiment, the vibration information in step S1 is acquired by a high-frequency pressure pulsation sensor 5 and a vibration acceleration sensor 7. The high-frequency pressure pulsation sensor 5 is located at the hydraulic oil outlet of the axial piston pump and can acquire the original pressure pulsation waveform signal and the instantaneous pressure pulsation waveform of the outlet fluid in real time. Specifically, the high-frequency pressure pulsation sensor 5 can be fixed to the outlet end of the distribution plate 8. The vibration acceleration sensor 7 is located on the swashplate 3 and is used to detect vibration acceleration signals transmitted to the swashplate 3. The vibration signals acquired by the high-frequency pressure pulsation sensor 5 and the vibration acceleration sensor 7 are synchronously transmitted to the controller 6, and then step S2 is performed.

[0041] In step S2, controller 6 performs real-time spectrum analysis on the received vibration signal. Through bandpass filtering and Fast Fourier Transform (FFT), it separates the amplitude A, frequency f, and phase ϕ of the fundamental wave and main harmonic components in the pressure pulsation waveform, extracting multimodal pulsation parameters such as the dominant vibration frequency, real-time phase, amplitude, and vibration acceleration characteristics of the pressure pulsation. Subsequently, the prediction model, based on the built-in machine learning prediction algorithm and combining historical operating data with the current operating conditions (i.e., the real-time acquired vibration information), predicts the future pressure pulsation trend. Finally, based on the preset force and magnetic coupling model and multimodal parameters, it calculates the reverse target force required to counteract the excitation force at future moments.

[0042] In this embodiment, based on the target force obtained in step S2, in step S3, the controller 6 combines the active waveform cancellation algorithm to generate a drive current signal corresponding to the drive current, and adjusts the direction and magnitude of the first magnetic field in real time; the drive current is ,in, The effective magnetic circuit length of coil assembly 4, This refers to the total number of turns of the annular electromagnetic coil within coil assembly 4. The permeability of free space, The force-to-magnetic field conversion coefficient, For the purpose of force.

[0043] In step S3, controller 6 can also calculate the propagation delay τ of the pressure wave from the vibration message acquisition location to the slipper 1 based on the piston pump's rotational speed and pressure pulsation frequency, and perform phase correction on the output phase of the drive current signal. At this time, the real-time drive current is: And target force With excitation force The magnitudes of the forces are equal, but their directions are opposite; the excitation force... Where k is the overall force transmission coefficient. This represents the equivalent working area of ​​the plunger pump. This represents the predicted instantaneous pressure pulsation value at the plunger pump outlet.

[0044] It also includes step S4: the controller 6 records the actual vibration message after the reaction force compensation in step S3 at the next moment, and verifies the vibration reduction effect. By comparing the difference between the actual vibration and the preset target, it adaptively adjusts the parameters of the prediction model (including the internal parameters of the prediction model and the machine learning algorithm) to achieve closed-loop online learning and continuous performance optimization.

[0045] This embodiment provides an active vibration reduction method for an axial piston pump based on magnetic reverse excitation, such as... Figure 1 and Figure 6 As shown, its working principle is as follows:

[0046] The high-frequency pressure pulsation sensor 5 collects the instantaneous pressure pulsation value at the plunger pump outlet in real time. This pressure fluctuation, after being transmitted through the fluid and mechanical structure, is converted into axial hydraulic excitation force on the slipper 1. This process involves energy transfer efficiency and time delay, and its mathematical model can be expressed as:

[0047]

[0048] Wherein, k is the comprehensive force transmission coefficient, a dimensionless number, and its value is usually between 0 and 1. It is used to reflect the energy transmission loss from the pressure signal detection point to the force point of the slipper 1. The equivalent working area of ​​the plunger is expressed in square millimeters (mm). 2 The calculation formula is: , where d is the plunger diameter; τ is the equivalent phase delay time from the pressure detection point to the action point of slipper 1, in seconds (s).

[0049] To completely counteract this excitation force, a target counteracting force of equal magnitude and opposite direction needs to be generated. The target force, also known as the objective force, is expressed mathematically as follows:

[0050]

[0051] Target Force This is achieved through the interaction between the magnetic field generated by the coil assembly 4 and the permanent magnet assembly 2. Near the small displacement operating point, the axial magnetic force acting on the slipper 1... The magnetic induction intensity generated by the coil at the working air gap This can be approximated as a linear relationship. Therefore, to generate the target force... The magnetic induction intensity that coil assembly 4 needs to generate It should meet the following requirements:

[0052]

[0053] Wherein, G is the force-magnetic field conversion coefficient, with the unit being Tesla per Newton (T / N). Its value can be obtained through magnetic circuit theory analysis and calculation or through experimental calibration on the actual system. A quantitative relationship between the magnetic field strength generated by the electromagnetic coil and the magnetic force that finally acts on the slipper 1 is established.

[0054] For the coil assembly 4 embedded in the surface of the swash plate 3, according to Ampere's circuital law, under ideal conditions where leakage flux is negligible and the magnetic circuit is uniform and unsaturated, the magnetic induction intensity it generates is... With drive current satisfy:

[0055]

[0056] in, The effective magnetic circuit length is expressed in meters (m). This represents the total number of turns in the toroidal electromagnetic coil, a design-defined value. The permeability of free space is approximately 4π × 10⁻⁶. -7 H / m, since the main path of the magnetic circuit in this invention is an air gap and a non-ferromagnetic material, with a relative permeability close to 1, therefore H / m is adopted. .

[0057] Therefore, in order to generate target force Required real-time drive current The specific expression is:

[0058]

[0059] Furthermore, considering that controller 6 uses machine learning algorithms to predict pressure pulsations in advance, i.e. Alternative To compensate for the delay τ, combined with the formula: This yields the complete control law for feedforward predictive control, which directly calculates the drive current from the pressure pulsation signal. The specific formula is as follows:

[0060]

[0061] This formula quantitatively describes the core control relationship from sensing pressure pulsations to generating an active canceling current, embodying the intelligent feedforward and phase compensation control strategy of this invention. The output current at the current moment is intended to cancel the excitation force at future moments. Mathematically, Indicates real-time output. This indicates the feedforward basis, and the combination of the two enables precise early cancellation of hydraulic excitation force. The complete control logic of this invention, from pressure signal acquisition and prediction to target force calculation and drive current generation, ensures that the target force can accurately and in real-time cancel the excitation force caused by pressure pulsation, thereby effectively suppressing the vibration of the axial piston pump.

[0062] Example 2

[0063] This embodiment provides an active vibration damping device for an axial piston pump based on magnetic reverse excitation, which can realize the method described above. It includes a slipper 1 and a swashplate 3. The swashplate 3 is provided with a coil assembly 4 at a position corresponding to the oil discharge area of ​​the piston pump. The slipper 1 is provided with a permanent magnet assembly 2. It also includes a detection assembly, which is used to collect vibration messages and transmit the vibration messages to a controller 6. The controller 6 is signal-connected to the coil assembly 4, which is used to receive vibration messages and generate a driving current to control the generation direction and magnitude of the first magnetic field in real time to achieve vibration damping.

[0064] The detection components include a high-frequency pressure pulsation sensor 5 and a vibration acceleration sensor 7. Specifically, the high-frequency pressure pulsation sensor 5 is installed in the pump outlet pipeline and is a piezoelectric dynamic pressure sensor with a resonant frequency of not less than 50kHz, with a sampling frequency set to 100kHz. The vibration acceleration sensor 7 is an ICP-type accelerometer with a range of ±500g and a frequency range of 0-10kHz, installed on a rigid part of the back of the swashplate 3. All sensor output signals are transmitted to the controller 6 via shielded cables.

[0065] During operation, the high-frequency pressure pulsation sensor 5 and the vibration acceleration sensor 7 monitor the system status in real time. The controller 6 quickly processes and generates intelligently predicted drive current, controlling the coil assembly 4 to produce a dynamically alternating first magnetic field at a specific moment. This first magnetic field interacts with the permanent magnet assembly 2 on the head of the slipper 1, which happens to be in the area, generating a dynamic magnetic reaction force on the slipper 1. This force is equal in magnitude, opposite in direction, and synchronized in time with the hydraulic excitation force transmitted to the slipper 1, thereby achieving real-time and precise cancellation of vibration.

[0066] The controller 6 is electrically connected to the high-frequency pressure pulsation sensor 5, the vibration acceleration sensor 7, and the coil assembly 4, respectively. By generating an alternating drive current signal with the opposite phase to the pressure pulsation waveform, the coil assembly 4 generates a local dynamic alternating magnetic field (first magnetic field) whose direction and magnitude change with time. This magnetic field interacts with the second magnetic field generated by the permanent magnet assembly 2, generating a dynamic magnetic reaction force between the slipper 1 and the swashplate 3, thereby counteracting the excitation force transmitted to the slipper 1 by the pressure pulsation in the plunger cavity in real time.

[0067] The controller 6 includes a phase-locking module, an amplitude matching module, and a phase delay compensation module for signal connections. It can extract pulsation parameters, including the dominant vibration frequency, real-time phase, amplitude, and vibration acceleration characteristics, based on vibration information. It also includes a digital signal processor (DSP) with a built-in machine learning model that can predict future pulsation trends based on these parameters. The phase-locking module tracks the phase of the pressure pulsation waveform in real time, ensuring that the magnetic force generated by the output current lags behind the excitation force by 180 degrees. The amplitude matching module adjusts the current gain according to multimodal parameters and system operating conditions, making the magnetic force amplitude approximate the excitation force amplitude. The phase delay compensation module is configured to calculate the sound propagation delay τ of the pressure wave from the high-frequency pressure pulsation sensor 5 installation position to the slipper 1 position based on the piston pump speed and pressure pulsation frequency, and to perform lead correction on the output phase of the drive current, ensuring that the generated dynamic magnetic reaction force and hydraulic excitation force are precisely aligned in the time domain. The DSP executes a neural network-based machine learning prediction algorithm to pre-calculate future pulsation parameters based on historical multimodal data.

[0068] like Figure 4 and Figure 5As shown in the figure, several first mounting grooves for mounting the permanent magnet assembly 2 are provided along the axial direction of the head of the slipper 1. Each first mounting groove is distributed in a variable-diameter spiral shape. The permanent magnet assembly 2 includes several magnet block units, and the distribution radius of each magnet block unit increases in the direction close to the plunger pump. Each magnet block unit adopts a variable-diameter spiral Halbach magnet array distribution, which is composed of fan-shaped magnets arranged discretely along the spiral trajectory. The spiral trajectory is at least divided into three distribution levels of the first radius (r1), the second radius (r2), and the third radius (r3) along the axial height of the head of the slipper 1, and r1 < r2 < r3, with a gradient increase, so as to form a conformal coating structure that conforms to the outer contour of the head of the slipper 1. The magnetization directions of the magnet block units are arranged to rotate at a specific angle, so that the magnetic field on the side facing the swash plate 3 of the permanent magnet assembly 2 is enhanced, while the magnetic field on the side of the body of the slipper 1 is weakened; the permanent magnet assembly 2 includes a high-energy permanent magnet core embedded in the head of the slipper 1 and a high-permeability alloy pole shoe covering the surface of the permanent magnet core; the high-permeability alloy pole shoe is used to converge magnetic flux and protect the high-energy permanent magnet core inside; the permanent magnet assembly 2 is distributed at equal intervals along the spiral of the head of the slipper 1, and the magnetization direction is perpendicular to the head of the slipper 1.

[0069] As Figure 2 and Figure 3 shown in the figure, the swash plate 3 is provided with a second mounting groove corresponding to the coil assembly 4 in the oil discharge area of the plunger pump. The second mounting groove is fan-shaped. In this embodiment, a fan-shaped shallow second mounting groove with a depth of 3.5 mm and a width of 8 mm is prefabricated below the working surface of the corresponding high-pressure oil discharge area of the swash plate 3. Correspondingly, the coil assembly 4 adopts a fan-shaped, independently packaged modular structure and is only distributed in the arc area of the swash plate 3 that bears high-pressure loads. The coil assembly 4 is a coreless high-frequency coil assembly 4, which includes at least one group of flat printed circuit board (PCB) coils or hollow flat multi-layer coils wound with Litz wire. The coil assembly 4 is embedded in the shallow second mounting groove prefabricated on the surface of the swash plate 3 and is encapsulated and cured by epoxy resin. The surface of the encapsulation is sprayed with a 0.2-mm-thick silicon nitride ceramic wear-resistant protective layer after grinding to maintain the flatness of the plane of the swash plate 3; the coil assembly 4 is fixed in the second mounting groove in a detachable manner, and the upper surface of the coil assembly 4 is covered with a wear-resistant coating to improve the reliability and durability of long-term operation. In this embodiment, the coil assembly 4 is a hollow flat coil wound with multiple strands of Litz wire, with 150 turns per single coil and a DC resistance of about 2 Ω. The coil is integrally encapsulated and cured by high-temperature-resistant epoxy resin through a vacuum potting process to form an independent module.

[0070] An annular cooling channel is also provided inside the swash plate 3. The cooling channel can be connected to a fan. The cooling channel is arranged below the second mounting groove, and forced air cooling is realized through devices such as an external centrifugal fan, driving air to circulate in the cooling channel, and timely taking away the heat generated when the coil assembly 4 works, ensuring that the working temperature of the coil does not exceed 80 °C, and ensuring the long-term stable operation of the coil assembly 4.

[0071] The above embodiments are only for illustrating the technical concept and features of the present invention, and are intended to enable those skilled in the art to understand and implement the present invention. They should not be construed as limiting the scope of protection of the present invention. All equivalent changes or modifications made in accordance with the spirit and essence of the present invention should be covered within the scope of protection of the present invention.

Claims

1. A method for active vibration reduction of an axial piston pump based on magnetic reverse excitation, characterized in that, include. S1. Real-time acquisition of vibration information, including pressure pulsation data at the outlet of the plunger pump and vibration signals transmitted to the swashplate; S2. The controller extracts the pulsation parameters of the vibration information, then predicts the pulsation parameters at the next moment based on the real-time pulsation parameters using a prediction model, and then calculates the target force required to counteract the excitation force at the next moment. S3. The controller controls the current flowing through the coil assembly based on the target force, so that it generates a first magnetic field; the permanent magnet assembly in the slipper generates a second magnetic field, and the coil assembly is set in the swashplate. Through the interaction of the first magnetic field and the second magnetic field, a reaction force is generated to counteract the excitation force and suppress the vibration of the slipper.

2. The active vibration reduction method for an axial piston pump based on magnetic reverse excitation as described in claim 1, characterized in that, The target force and the excitation force are equal in magnitude and opposite in direction. In step S3, the controller combines the active waveform cancellation algorithm to generate a drive current signal corresponding to the drive current, and adjusts the generation direction and magnitude of the first magnetic field in real time.

3. The active vibration reduction method for an axial piston pump based on magnetic reverse excitation as described in claim 2, characterized in that, The controller can also calculate the propagation delay τ of the pressure wave from the acquisition location of the vibration message to the slipper, and perform phase correction on the output phase of the drive current signal.

4. The active vibration reduction method for an axial piston pump based on magnetic reverse excitation as described in claim 3, characterized in that, The driving current is ,in, The effective magnetic circuit length of the coil assembly is... The total number of turns of the annular electromagnetic coil within the coil assembly. The permeability of free space, The force-to-magnetic field conversion coefficient, For the comprehensive force transmission coefficient, This refers to the equivalent working area of ​​the plunger pump. The predicted instantaneous pressure pulsation value at the outlet of the plunger pump. .

5. The active vibration reduction method for an axial piston pump based on magnetic reverse excitation as described in claim 1, characterized in that, It also includes step S4: the controller records the actual vibration message after the reaction force compensation in step S3 at the next moment, and adaptively adjusts the parameters of the prediction model.

6. An active vibration damping device for an axial piston pump based on magnetic reverse excitation, capable of implementing the method described in any one of claims 1-5, characterized in that, The system includes a slipper and a swashplate. The swashplate has a coil assembly at a position corresponding to the oil discharge area of ​​the plunger pump, and the slipper is equipped with a permanent magnet assembly. The system also includes a detection assembly for collecting vibration messages and transmitting them to the controller. The controller is connected to the coil assembly to receive the vibration messages and generate the drive current, thereby controlling the direction and magnitude of the first magnetic field in real time to achieve vibration reduction.

7. The active vibration damping device for an axial piston pump based on magnetic reverse excitation as described in claim 6, characterized in that, The controller includes a phase-locked module, an amplitude matching module, and a phase delay compensation module connected by signals. It is capable of extracting the pulsation parameters, including the dominant vibration frequency, real-time phase, amplitude, and vibration acceleration characteristics, based on the vibration information. It also includes a digital signal processor, which contains the machine learning model and is capable of predicting future pulsation trends based on the pulsation parameters.

8. The active vibration damping device for an axial piston pump based on magnetic reverse excitation as described in claim 6, characterized in that, The head of the slipper is provided with a plurality of first mounting slots along its axial direction for mounting the permanent magnet assembly. Each of the first mounting slots is distributed in a variable diameter spiral shape. The permanent magnet assembly includes a plurality of magnetic block units, and the distribution radius of each magnetic block unit increases in the direction close to the plunger pump.

9. The active vibration damping device for an axial piston pump based on magnetic reverse excitation as described in claim 6, characterized in that, The swash plate has a second mounting groove corresponding to the coil assembly in the oil discharge area of ​​the plunger pump. The second mounting groove is fan-shaped.

10. The active vibration damping device for an axial piston pump based on magnetic reverse excitation as described in claim 6, characterized in that, The swash plate is also equipped with an annular cooling channel, which can be connected to a fan.

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