Double-eccentric-wheel inertia actuator for targeted vibration reduction of railway vehicle bogie

Abstract

The invention discloses a double-eccentric-wheel inertia actuator for targeted vibration reduction of a railway vehicle bogie, vibration of a bogie frame can be restrained through eccentric mass inertia force coupling of two mass center offset wheels, and meanwhile the excitation frequency, the amplitude and the phase of the double-eccentric-wheel inertia actuator can be dynamically adjusted according to actual requirements. Comprising a double-eccentric-wheel vibration mechanism which comprises a supporting mechanism installed on the connecting rigidity during use, a first centroid offset wheel with a first centroid offset amount and a second centroid offset wheel with a second centroid offset amount, and the first centroid offset wheel and the second centroid offset wheel are installed on the supporting mechanism and arranged in a bilateral symmetry mode; the double-eccentric-wheel vibration frequency phase control mechanism is connected with the first eccentric wheel and the second eccentric wheel so as to control the first eccentric wheel and the second eccentric wheel to synchronously and reversely rotate at the same set rotating speed; and the double-eccentric-wheel vibration amplitude control mechanism is connected with the first eccentric mass and the second eccentric mass so as to control the first centroid offset and the second centroid offset to reach the same set centroid offset.

Description

Technical Field

[0001] The present invention relates to the technical field of vibration damping control for railway vehicle bogies, and particularly to a double eccentric wheel inertial actuator for targeted vibration damping of railway vehicle bogies. Background Art

[0002] With the operating speed of high-speed multiple units approaching 400 km / h, under the action of multi-source excitation and multi-modal strong coupling, the vibration problem of the bogie frame becomes increasingly prominent, seriously affecting the running safety and riding comfort. In the existing vibration damping control technologies for railway vehicle bogies, the passive vibration damping structure is simple but has limited effect, while the active vibration damping (mainly the active suspension system, semi-active suspension system, etc.) has better effect but is costly and complex to control.

[0003] The available prior arts for reference include: 1) Patent Publication No. CN102616245A (Title: Train Bogie Semi-Active Vibration Damper Control Device and System and Its Control Method); 2) Patent Publication No. CN102069813A (Title: Switch-Type Semi-Active Suspension System); 3) Patent Publication No. CN107848548A (Title: Vibration Damping Device for Railway Vehicles). Summary of the Invention

[0004] The object of the present invention is to provide a double eccentric wheel inertial actuator for targeted vibration damping of railway vehicle bogies. The double eccentric wheel inertial actuator can suppress the vibration of the bogie frame through the coupling of the eccentric mass inertial forces of two centroid offset wheels, and at the same time, its excitation frequency, amplitude and phase can be dynamically adjusted according to actual needs, thereby providing an innovative solution for vibration damping of railway vehicle bogies.

[0005] A double eccentric wheel inertial actuator for targeted vibration reduction of railway vehicle bogies, which is installed on the bogie frame through connection stiffness during use; it includes: a double eccentric wheel vibration mechanism, which includes a support mechanism installed on the connection stiffness during use and a first centroid offset wheel and a second centroid offset wheel installed on the support mechanism and symmetrically arranged left and right. The first centroid offset wheel has a first eccentric mass that can be displaced and adjusted in the radial direction of the rotation center of the first centroid offset wheel. The radial distance between the centroid of the first eccentric mass and the rotation center of the first centroid offset wheel is the first centroid offset amount. The second centroid offset wheel has a second eccentric mass that can be displaced and adjusted in the radial direction of the rotation center of the second centroid offset wheel. The radial distance between the centroid of the second eccentric mass and the rotation center of the second centroid offset wheel is the second centroid offset amount; a double eccentric wheel vibration frequency and phase control mechanism, connected to the first eccentric wheel and the second eccentric wheel to control the first eccentric wheel and the second eccentric wheel to rotate synchronously and reversely at the same set speed; a double eccentric wheel vibration amplitude control mechanism, connected to the first eccentric mass and the second eccentric mass to control the first centroid offset amount and the second centroid offset amount to reach the same set centroid offset amount.

[0006] As an optimization and / or instantiation of the above double eccentric wheel inertial actuator, further: the first centroid offset wheel and the second centroid offset wheel are symmetrically arranged left and right on the support mechanism, so that when the double eccentric wheel vibration mechanism operates, it can be controlled by the double eccentric wheel vibration frequency and phase control mechanism and the double eccentric wheel vibration amplitude control mechanism to achieve: i) the centrifugal force generated by the first centroid offset wheel is equal to the centrifugal force generated by the second centroid offset wheel; ii) the horizontal component of the centrifugal force generated by the first centroid offset wheel and the horizontal component of the centrifugal force generated by the second centroid offset wheel completely cancel each other out on the support mechanism; and iii) the vertical component of the centrifugal force generated by the first centroid offset wheel and the vertical component of the centrifugal force generated by the second centroid offset wheel are superimposed on the support mechanism to form a vertical control force, and the variation relationship of the vertical control force with time can be represented by the following sine function: F 0 =2×F S ×sin(ωt±θ) , where, F 0 is the vertical control force, F S is the centrifugal force generated by the first centroid offset wheel or the centrifugal force generated by the second centroid offset wheel, ω is the rotational angular velocity of the first centroid offset wheel or the rotational angular velocity of the second centroid offset wheel, t represents time, θ is the rotational phase of the centroid of the first eccentric mass or the rotational phase of the centroid of the second eccentric mass.

[0007] As an optimization and / or instantiation of the above double eccentric inertial actuator, further: when in use, the control of the set rotational speed by the double eccentric vibration frequency and phase control mechanism enables the F 0 change frequency in the sine function to be consistent with the dominant mode resonance frequency of the bogie frame and F 0 the instantaneous phase of the sine function to be opposite to the instantaneous phase of the dominant mode resonance of the bogie frame.

[0008] As an optimization and / or instantiation of the above double eccentric inertial actuator, further: when in use, first, the control of the set rotational speed by the double eccentric vibration frequency and phase control mechanism enables the F 0 change frequency in the sine function to be consistent with the dominant mode resonance frequency of the bogie frame and F 0 the instantaneous phase of the sine function to be opposite to the instantaneous phase of the dominant mode resonance of the bogie frame. Then, the double eccentric vibration amplitude control mechanism adjusts the set centroid offset so that the magnitude of the vertical control force reaches a level that can technically and effectively suppress the vertical vibration of the bogie frame.

[0009] As an optimization and / or instantiation of the above double eccentric inertial actuator, further: the double eccentric vibration frequency and phase control mechanism includes a driving motor and a driving gear set. The driving gear set includes a first driving gear and a second driving gear. The first driving gear is connected to the output shaft of the driving motor. The second driving gear has the same number of teeth as the first driving gear and meshes with each other. The first centroid offset wheel is coaxially and fixedly connected to the first driving gear to form a first rotating assembly. The second centroid offset wheel is coaxially and fixedly connected to the second driving gear to form a second rotating assembly. The first rotating assembly and the second rotating assembly are rotationally supported on the support mechanism.

[0010] As an optimization and / or instantiation of the above double eccentric inertial actuator, further: the driving motor is a servo motor.

[0011] As an optimization and / or instantiation of the above double eccentric inertial actuator, further: the first centroid offset wheel has a first centroid offset wheel body. A first lead screw mechanism is provided on the first centroid offset wheel body. The first eccentric mass is installed on the first lead screw mechanism as a nut that can linearly reciprocate in the first lead screw mechanism. The second centroid offset wheel has a second centroid offset wheel body. A second lead screw mechanism is provided on the second centroid offset wheel body. The second eccentric mass is installed on the second lead screw mechanism as a nut that can linearly reciprocate in the second lead screw mechanism. The double eccentric vibration amplitude control mechanism controls the first centroid offset amount by controlling the rotation of the lead screw in the first lead screw mechanism and controls the second centroid offset amount by controlling the rotation of the lead screw in the second lead screw mechanism.

[0012] As an optimization and / or instantiation of the above-mentioned double eccentric inertial actuator, further: the double eccentric vibration amplitude control mechanism includes an amplitude modulation motor set, and the amplitude modulation motor set includes a first amplitude modulation motor and a second amplitude modulation motor. The first amplitude modulation motor is drivingly connected to a first lead screw mechanism, and the second amplitude modulation motor is drivingly connected to a second lead screw mechanism.

[0013] As an optimization and / or instantiation of the above-mentioned double eccentric inertial actuator, further: the first amplitude modulation motor is coaxially arranged with the rotation center of the first centroid offset wheel, and the first amplitude modulation motor is drivingly connected to the first lead screw mechanism through a first bevel gear transmission mechanism; the second amplitude modulation motor is coaxially arranged with the rotation center of the second centroid offset wheel, and the second amplitude modulation motor is drivingly connected to the second lead screw mechanism through a second bevel gear transmission mechanism.

[0014] As an optimization and / or instantiation of the above-mentioned double eccentric inertial actuator, further: the double eccentric vibration amplitude control mechanism includes two slip rings, and both of the two slip rings include a fixed part and a rotating part. The fixed parts of the two slip rings are used for connecting to an external power supply. The rotating part of one slip ring rotates with the rotation of the first amplitude modulation motor to supply power to the first amplitude modulation motor, and the rotating part of one slip ring rotates with the rotation of the second amplitude modulation motor to supply power to the second amplitude modulation motor.

[0015] In the above-mentioned double eccentric inertial actuator of the present invention, since the first centroid offset wheel and the second centroid offset wheel are symmetrically arranged left and right, the double eccentric vibration frequency and phase control mechanism controls the first centroid offset wheel and the second centroid offset wheel to rotate synchronously and in opposite directions at the same set rotational speed, and the double eccentric vibration amplitude control mechanism controls the first centroid offset amount and the second centroid offset amount to reach the same set centroid offset amount. Therefore, the double eccentric inertial actuator of the present invention can suppress the vibration of the bogie frame through the coupling of the eccentric mass inertia force of the first centroid offset wheel and the eccentric mass inertia force of the second centroid offset wheel. At the same time, its excitation frequency, amplitude and phase can all be dynamically adjusted according to actual needs (the excitation frequency and phase are controlled by the double eccentric vibration frequency and phase control mechanism, while the excitation amplitude is controlled by the double eccentric vibration amplitude control mechanism), thereby providing an innovative solution for the vibration reduction of railway vehicle bogies.

[0016] The following further describes the present invention in conjunction with the drawings and specific embodiments. The additional aspects and advantages provided by the present invention will be partially given in the following description, partially become obvious from the following description, or be understood through practice. Description of the Drawings

[0017] The drawings forming a part of this specification are used to assist in understanding the present invention. The content provided in the drawings and the related descriptions in this specification can be used to explain the present invention, but do not constitute an improper limitation to the present invention.

[0018] Figure 1 This is a schematic structural diagram of a double eccentric wheel inertial actuator according to an embodiment of the present invention.

[0019] Figure 2 is Figure 1 a view of the double eccentric wheel inertial actuator shown in a top-down perspective.

[0020] Figure 3 is Figure 1 a view of the double eccentric wheel inertial actuator shown in a right-side perspective.

[0021] Figure 4 is Figure 1 a schematic diagram of the working principle of the double eccentric wheel inertial actuator shown.

[0022] In the figure, the markings are: drive motor 1, first drive gear 2a, second drive gear 2b, drive gear set 2, centroid offset wheel 3, first centroid offset wheel 3a, second centroid offset wheel 3b, eccentric mass 4, first eccentric mass 4a, second eccentric mass 4b, first lead screw mechanism 5a, second lead screw mechanism 5b, amplitude modulation motor set 6, first amplitude modulation motor 6a, second amplitude modulation motor 6b, slip ring 7, bearing 8, bearing housing 9, first bevel gear 10a, second bevel gear 10b, third bevel gear 10c, fourth bevel gear 10d, connection stiffness 11, bogie frame 12, vibration sensor 13, control system 14, actuator housing 15. Specific embodiments

[0023] The present invention will be clearly and completely described below with reference to the accompanying drawings. Those of ordinary skill in the art will be able to implement the present invention based on these descriptions. Before describing the present invention with reference to the accompanying drawings, it should be particularly noted that: The technical solutions and technical features provided in each part including the following description can be combined with each other without conflict. In addition, where possible, these technical solutions, technical features and related combinations can be given specific technical subjects and protected by relevant patents.

[0024] The embodiments of the present invention involved in the following description are usually only some embodiments rather than all embodiments. All other embodiments obtained by those of ordinary skill in the art without creative efforts based on these embodiments should fall within the scope of patent protection.

[0025] The terms "comprising", "including", "having" and any variations thereof in this specification, the corresponding claims and the relevant parts are intended to cover non-exclusive inclusion. Other relevant terms and units can be reasonably interpreted based on the relevant content provided in this specification.

[0026] Figure 1 It is a schematic structural diagram of a double eccentric wheel inertial actuator according to an embodiment of the present invention. Figure 2 is Figure 1 a view of the double eccentric wheel inertial actuator shown in a top-down perspective. Figure 3 is Figure 1 a view of the double eccentric wheel inertial actuator shown in a right-side perspective. As Figures 1 - 3 shown, the double eccentric wheel inertial actuator includes three major parts: a double eccentric wheel vibration mechanism, a double eccentric wheel vibration frequency and phase control mechanism, and a double eccentric wheel vibration amplitude control mechanism.

[0027] The double eccentric wheel vibration mechanism includes a support mechanism and a first centroid offset wheel 3a and a second centroid offset wheel 3b that are symmetrically arranged left and right and mounted on the support mechanism. The first centroid offset wheel 3a and the second centroid offset wheel 3b can be collectively represented by Figure 1 the centroid offset wheel 3 in

[0028] The first centroid offset wheel 3a has a first eccentric mass 4a that can be displaced and adjusted in the radial direction of the rotation center of the first centroid offset wheel 3a. The radial distance between the centroid of the first eccentric mass 4a and the rotation center of the first centroid offset wheel 3a is the first centroid offset amount. The first centroid offset amount can be specifically represented by Figure 3 "r1" on the first centroid offset wheel 3a in

[0029] The second centroid offset wheel 3b has a second eccentric mass 4b that can be displaced and adjusted in the radial direction of the rotation center of the second centroid offset wheel 3b. The radial distance between the centroid of the second eccentric mass 4b and the rotation center of the second centroid offset wheel 3b is the second centroid offset amount. The second centroid offset amount can be specifically represented by Figure 3 "r2" on the second centroid offset wheel 3b in

[0030] Among them, the first eccentric mass 4a and the second eccentric mass 4b can be collectively represented by Figure 1 the eccentric mass 4 in

[0031] The double eccentric wheel vibration frequency and phase control mechanism is connected to the first centroid offset wheel 3a and the second centroid offset wheel 3b to control the first centroid offset wheel 3a and the second centroid offset wheel 3b to rotate synchronously and in opposite directions at the same set rotational speed.

[0032] The essence of the double eccentric wheel vibration frequency and phase control mechanism is to control the rotation behavior of the first centroid offset wheel 3a and the second centroid offset wheel 3b. By ensuring that the two wheels rotate synchronously and in opposite directions at the same set rotational speed, the expected vibration effect can be generated. This rotational control can be achieved through various technical solutions, such as using a synchronous rotation control system composed of two servo motors and a precision controller, etc.

[0033] The double eccentric wheel vibration amplitude control mechanism is connected to the first eccentric mass 4a and the second eccentric mass 4b to control the first centroid offset amount and the second centroid offset amount to reach the same set centroid offset amount.

[0034] The essence of the double eccentric wheel vibration amplitude control mechanism is to achieve precise adjustment of the positions of the first eccentric mass 4a and the second eccentric mass 4b. By controlling the first centroid offset amount and the second centroid offset amount to reach the same set value, the vibration amplitude generated by the double eccentric wheel inertial actuator can be precisely controlled. The double eccentric wheel vibration amplitude control mechanism can be achieved through various technical solutions, including hydraulic or pneumatic adjustment mechanisms, precision mechanical displacement systems, etc.

[0035] Figure 4 For Figure 1 the schematic diagram of the working principle of the double eccentric wheel inertial actuator shown. Combining Figure 4 as shown, when the above double eccentric wheel inertial actuator is in use, its support mechanism is installed on the bogie frame 12 through the connection stiffness 11.

[0036] Since the first centroid offset wheel 3a has the first eccentric mass 4a, there is a first centroid offset amount between the centroid of the first eccentric mass 4a and the rotation center of the first centroid offset wheel 3a. The first centroid offset amount is essentially the centroid offset amount of the first centroid offset wheel 3a. Therefore, when the first eccentric mass 4a rotates around the rotation center of the first centroid offset wheel 3a, a periodically changing centrifugal force (eccentric mass inertia force) will be generated, which will in turn cause the first centroid offset wheel 3a to vibrate.

[0037] Similarly, since the second centroid offset wheel 3b has the second eccentric mass 4b, there is a second centroid offset amount between the centroid of the second eccentric mass 4b and the rotation center of the second centroid offset wheel 3b. The second centroid offset amount is essentially the centroid offset amount of the second centroid offset wheel 3a. Therefore, when the second eccentric mass 4b rotates around the rotation center of the second centroid offset wheel 3b, a periodically changing centrifugal force (eccentric mass inertia force) will be generated, which will in turn cause the second centroid offset wheel 3b to vibrate.

[0038] Taking the first centroid offset wheel 3a as an example, the specific parameter adjustment mechanisms for generating vibration of the first centroid offset wheel 3a are described as follows. The vibration frequency of the first centroid offset wheel 3a is directly determined by the rotational speed of the output shaft of the power source (usually the driving motor 1 described below) in the double eccentric wheel vibration frequency and phase control mechanism. When the power source adjusts the rotational speed, the rotational speed of the first centroid offset wheel 3a changes accordingly, thereby changing the vibration frequency; the vibration phase is jointly determined by the starting moment of the power source and the initial installation position of the first eccentric mass 4a. The initial phase can be set by adjusting the fixed angular position of the first eccentric mass 4a relative to the first centroid offset wheel 3a; while the vibration amplitude is mainly determined by the mass of the first eccentric mass 4a and the first centroid offset amount. The first centroid offset amount can be adjusted through the double eccentric wheel vibration amplitude control mechanism, thereby changing the magnitude of the centrifugal force and realizing the control of the vibration amplitude. The parameter adjustment mechanisms for generating vibration of the second centroid offset wheel 3b can be known by the same reasoning.

[0039] Since the first centroid offset wheel 3a and the second centroid offset wheel 3b are symmetrically arranged left and right, the double eccentric wheel vibration frequency and phase control mechanism controls the first centroid offset wheel 3a and the second centroid offset wheel 3b to rotate synchronously and in opposite directions at the same set rotational speed, and the double eccentric wheel vibration amplitude control mechanism controls the first centroid offset amount and the second centroid offset amount to reach the same set centroid offset amount. Therefore, the above double eccentric wheel inertial actuator can suppress the vibration of the bogie frame through the coupling of the eccentric mass inertial forces of the first centroid offset wheel 3a and the second centroid offset wheel 3b. At the same time, its excitation frequency, amplitude, and phase can all be dynamically adjusted according to actual needs (the excitation frequency and phase are controlled by the double eccentric wheel vibration frequency and phase control mechanism, while the excitation amplitude is controlled by the double eccentric wheel vibration amplitude control mechanism).

[0040] More specifically, when the first centroid offset wheel 3a and the second centroid offset wheel 3b are symmetrically arranged left and right and the first centroid offset wheel 3a and the second centroid offset wheel 3b rotate synchronously and in opposite directions at the same set rotational speed, it can make the eccentric mass inertial forces of the first centroid offset wheel 3a and the second centroid offset wheel 3b couple to generate a control force in a specific direction (mainly the vertical direction) and weaken the interference forces in other directions, thereby realizing the targeted suppression of the vertical vibration of the bogie frame 12.

[0041] Combined with Figure 4 As shown, an ideal working state of the above double eccentric wheel inertial actuator is that the first centroid offset wheel 3a and the second centroid offset wheel 3b are symmetrically arranged left and right on the support mechanism, which can enable the double eccentric wheel vibration mechanism to achieve the following under the control of the double eccentric wheel vibration frequency and phase control mechanism and the double eccentric wheel vibration amplitude control mechanism: i) The magnitude of the centrifugal force generated by the first centroid offset wheel 3a is equal to the magnitude of the centrifugal force generated by the second centroid offset wheel 3b; ii) The horizontal components of the centrifugal forces generated by the first centroid offset wheel 3a and the second centroid offset wheel 3b are completely cancelled out on the support mechanism; iii) The vertical components of the centrifugal forces generated by the first centroid offset wheel 3a and the second centroid offset wheel 3b are superimposed on the support mechanism to form a vertical control force, and the variation relationship of the vertical control force with time can be expressed by the following sine function: F 0 =2×F S ×sin(ωt±θ) , where F 0 is the vertical control force, F S is the centrifugal force generated by the first centroid offset wheel 3a or the second centroid offset wheel 3b, ω is the rotational angular velocity of the first centroid offset wheel 3a or the second centroid offset wheel 3b, t represents time, θ represents the rotational phase of the centroid of the first eccentric mass 4a or the rotational phase of the centroid of the second eccentric mass 4b.

[0042] Among them, the centrifugal force generated by the first centroid offset wheel 3a or the second centroid offset wheel 3b F S can be expressed according to the centrifugal force calculation formula as F S =m 1 ×ω 2 ×r , where m 1 represents the mass of the first eccentric mass 4a or the second eccentric mass 4b.

[0043] When the double eccentric wheel inertial actuator is in the above ideal working state, the double eccentric wheel inertial actuator only generates a vertical control force F 0 and F 0 =2×F S ×sin(ωt±θ), This vertical control force without horizontal interference is transmitted to the bogie frame 12 through the connection stiffness 11, and can be accurately phase-matched with the vertical vibration of the bogie frame 12, thereby forming an effective vibration suppression effect.

[0044] To achieve the above ideal working state, the left-right symmetric arrangement of the first centroid offset wheel 3a and the second centroid offset wheel 3b must meet strict geometric symmetry, dynamic symmetry (same mass characteristics, strictly synchronous reverse rotation, etc.), geometric parameter accuracy (the first centroid offset amount is exactly equal to the second centroid offset amount, and the centroid offset directions are symmetric), control system symmetry (accurate frequency and phase control, and consistent adjustment of the first centroid offset amount and the second centroid offset amount), as well as dynamic balance and installation connection requirements (static and dynamic balance, symmetric connection stiffness).

[0045] To meet the requirements of the left-right symmetric arrangement of the first centroid offset wheel 3a and the second centroid offset wheel 3b, one of the key points is to ensure that the first centroid offset wheel 3a and the second centroid offset wheel 3b rotate strictly synchronously in the reverse direction and maintain an accurate phase relationship.

[0046] Based on this requirement, the double eccentric wheel vibration frequency and phase control mechanism can be designed as follows: The double eccentric wheel vibration frequency and phase control mechanism wheel set 2, the drive gear set 2 includes a first drive gear 2a and a second drive gear 2b. The first drive gear 2a is connected to the output shaft of the drive motor 1. The second drive gear 2b has the same number of teeth as the first drive gear 2a and meshes with each other. The first centroid offset wheel 3a is fixedly connected to the first drive gear 2a coaxially to form a first rotating assembly. The second centroid offset wheel 3b is fixedly connected to the second drive gear 2b coaxially to form a second rotating assembly. The first rotating assembly and the second rotating assembly are rotationally supported on the support mechanism.

[0047] Among them, the support mechanism may specifically include an actuator housing 15 and a bearing seat 9 located in the actuator housing 15. The first rotating assembly and the second rotating assembly are respectively installed in the actuator housing 15 through the corresponding bearing seats 9 and bearings 8.

[0048] Since the second drive gear 2b has the same number of teeth as the first drive gear 2a and meshes with each other, it can ensure that the transmission ratio is 1:1 and the rotation is in the reverse direction. Therefore, the above design not only ensures that the rotational speeds of the first centroid offset wheel 3a and the second centroid offset wheel 3b are strictly equal, but also realizes the synchronous reverse rotation of the first centroid offset wheel 3a and the second centroid offset wheel 3b through the first drive gear 2a and the second drive gear 2b meshing with it, providing an accurate mechanical guarantee for the complete cancellation of the horizontal component and the effective superposition of the vertical component.

[0049] The driving motor 1 preferably adopts a servo motor. The main reason is that the servo motor has high-precision speed and position closed-loop control capabilities, and can achieve precise control of speed, acceleration and phase, ensuring that the first mass center offset wheel 3a and the second mass center offset wheel 3b rotate synchronously in opposite directions at the same set speed and maintain an ideal phase relationship. In addition, the servo motor has a fast response speed, a wide speed regulation range, and excellent dynamic performance. It can quickly adjust the control parameters according to the vibration characteristics of different working conditions, which helps to achieve adaptive suppression of the vertical vibration of the bogie frame 12.

[0050] In an optional embodiment, the first center of mass offset wheel 3a has a first center of mass offset wheel body, a first screw mechanism 5a is provided on the first center of mass offset wheel body, and the first eccentric mass 4a is installed on the first screw mechanism 5a as a nut that can move linearly reciprocating in the first screw mechanism 5a; the second center of mass offset wheel 3b has a second center of mass offset wheel body, a second screw mechanism 5b is provided on the second center of mass offset wheel body, and the second eccentric mass 4b is installed on the second screw mechanism 5b as a nut that can move linearly reciprocating in the second screw mechanism 5b; the double eccentric wheel vibration amplitude control mechanism realizes the control of the first center of mass offset by controlling the rotation of the screw in the first screw mechanism 5a, and realizes the control of the second center of mass offset by controlling the rotation of the screw in the second screw mechanism 5b.

[0051] Specifically, the dual eccentric vibration amplitude control mechanism includes an amplitude modulation motor group 6, the amplitude modulation motor 6 includes a first amplitude modulation motor 6a and a second amplitude modulation motor 6b, the first amplitude modulation motor 6a is transmission connected to the first screw mechanism 5a, and the second amplitude modulation motor 6b is transmission connected to the second screw mechanism 5b.

[0052] The above optional implementation manner provides a mechanical transmission mechanism that can accurately control the first center of mass offset and the second center of mass offset. By designing the first eccentric mass 4a and the second eccentric mass 4b as movable nuts installed on the first screw mechanism 5a and the second screw mechanism 5b respectively, the first center of mass offset and the second center of mass offset are continuously adjustable. When the first screw mechanism 5a and the second screw mechanism 5b rotate, the first eccentric mass 4a and the second eccentric mass 4b move along the axis of their respective screws respectively, changing their distance from the rotation center of the first center of mass offset wheel 3a and the second center of mass offset wheel 3b, directly affecting the magnitude of the centrifugal force.

[0053] Among them, the first amplitude modulation motor 6a is coaxially arranged with the rotation center of the first center of mass offset wheel 3a, and the first amplitude modulation motor 6a is transmission connected to the first screw mechanism 5a through the first bevel gear transmission mechanism; the second amplitude modulation motor 6b is coaxially arranged with the rotation center of the second center of mass offset wheel 3b, and the second amplitude modulation motor 6b is transmission connected to the second screw mechanism 5b through the second bevel gear transmission mechanism.

[0054] The spatial structure in which the first amplitude modulation motor 6a and the second amplitude modulation motor 6b are respectively arranged coaxially with the rotation centers of the first centroid offset wheel 3a and the second centroid offset wheel 3b. Through the first bevel gear transmission mechanism (specifically including the mutually meshing first bevel gear 10a and the third bevel gear 10c) and the second bevel gear transmission mechanism (specifically including the mutually meshing second bevel gear 10b and the fourth bevel gear 10d), the rotational power of the first amplitude modulation motor 6a and the second amplitude modulation motor 6b is respectively transmitted to the first lead screw mechanism 5a and the second lead screw mechanism 5b, solving the technical problem of power transmission in the rotating coordinate system. Since the first amplitude modulation motor 6a is coaxially arranged with the rotation center of the first centroid offset wheel 3a, and the second amplitude modulation motor 6b is coaxially arranged with the rotation center of the second centroid offset wheel 3b, it effectively avoids the additional centrifugal force and dynamic balance problems generated by each amplitude modulation motor rotating at high speed with the corresponding centroid offset wheel.

[0055] In addition, the double eccentric wheel vibration amplitude control mechanism includes two slip rings 7. Both of these slip rings 7 include a fixed part and a rotating part. The fixed parts of the two slip rings 7 are used to connect to an external power supply. The rotating part of one slip ring 7 rotates with the rotation of the first amplitude modulation motor 6a to supply power to the first amplitude modulation motor 6a, and the rotating part of one slip ring 7 rotates with the rotation of the second amplitude modulation motor 6b to supply power to the second amplitude modulation motor 6b.

[0056] As Figure 4 shown, the specific implementation steps when using the above double eccentric wheel inertial actuator are as follows: First, install the double eccentric wheel inertial actuator on the bogie frame 12 through the connection stiffness 11 to ensure the firm connection between the double eccentric wheel inertial actuator and the bogie frame 12. Subsequently, arrange a vibration sensor 13 on the bogie frame 12 to monitor the vibration state of the bogie frame 12 in real time. The vibration sensor 13 is connected to the control system 14, and the control system 14 adjusts the working states of the drive motor 1 and the amplitude modulation motor group 6 in real time according to the feedback signal of the vibration sensor 13. During the vibration control process, first control the rotation speed and phase of the double eccentric wheel inertial actuator through the drive motor 1 to make the F 0 change frequency in the sine function consistent with the dominant mode resonance frequency of the bogie frame 12 and F 0The instantaneous phase of [the relevant quantity] is opposite to the instantaneous phase of the dominant mode resonance of the bogie frame 12. Then, the double eccentric wheel vibration amplitude control mechanism is used to adjust the set centroid offset, so that the magnitude of the vertical control force reaches a level that can effectively suppress the vertical vibration of the bogie frame 12 technically (usually, it is considered "effective" when the vertical vibration amplitude of the bogie frame 12 is reduced by more than 30% or the vibration energy density in a specific frequency range is significantly reduced). Finally, the vertical control force generated by the double eccentric wheel inertial actuator is used to suppress the vertical vibration of the bogie frame 12 and achieve active targeted control of the dominant mode resonance.

[0057] The dominant mode resonance refers to the dominant vibration modes exhibited by the bogie frame 12. These modes dominate in energy distribution, contribute the most to the structural dynamic response, often produce obvious resonance peaks at specific frequencies, and are likely to cause system instability and excessive vibration. When in the sine function F 0 the change frequency is consistent with the dominant mode resonance frequency of the bogie frame 12 and F 0 the instantaneous phase of [the relevant quantity] is opposite to the instantaneous phase of the dominant mode resonance of the bogie frame 12, an accurate "anti-vibration" force can be formed, effectively canceling the original vibration energy, significantly reducing the vibration amplitude of the bogie frame 12, improving the running smoothness and comfort of the train, while reducing structural fatigue damage and extending the service life of key components.

[0058] Through experimental verification, the above double eccentric wheel inertial actuator can reduce the vertical vibration amplitude of the bogie frame 12 and effectively suppress the dominant mode resonance.

[0059] The above describes the relevant content of the present invention. Those of ordinary skill in the art will be able to implement the present invention based on these descriptions. Based on the above content of this specification, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the scope of the present invention.

Claims

1. A double eccentric inertial actuator for targeted vibration reduction of railway vehicle bogies, characterized in that: When in use, it is mounted on a bogie frame (12) via a connection stiffness (11); it comprises: A double eccentric wheel vibration mechanism comprises a support mechanism installed on a connection stiffness (11) when in use, and a first mass center offset wheel (3a) and a second mass center offset wheel (3b) installed on the support mechanism and arranged symmetrically on the left and right, the first mass center offset wheel (3a) having a first eccentric mass (4a) capable of displacement adjustment in the radial direction of the rotation center of the first mass center offset wheel (3a), the radial distance between the mass center of the first eccentric mass (4a) and the rotation center of the first mass center offset wheel (3a) being a first mass center offset amount, the second mass center offset wheel (3b) having a second eccentric mass (4b) capable of displacement adjustment in the radial direction of the rotation center of the second mass center offset wheel (3b), the radial distance between the mass center of the second eccentric mass (4b) and the rotation center of the second mass center offset wheel (3b) being a second mass center offset amount; A double eccentric wheel vibration frequency phase control mechanism is connected to the first mass center offset wheel (3a) and the second mass center offset wheel (3b) to control the first mass center offset wheel (3a) and the second mass center offset wheel (3b) to rotate synchronously in opposite directions at the same set speed; The double eccentric wheel vibration amplitude control mechanism is connected to the first eccentric mass (4a) and the second eccentric mass (4b) to control the first mass center offset and the second mass center offset to reach the same set mass center offset.

2. A double eccentric wheel inertial actuator for targeted vibration reduction of a railway vehicle bogie as claimed in claim 1, characterized in that: The first mass center offset wheel (3a) and the second mass center offset wheel (3b) are symmetrically arranged on the support mechanism, so that when the double eccentric wheel vibration mechanism is in operation, it can be controlled by the double eccentric wheel vibration frequency phase control mechanism and the double eccentric wheel vibration amplitude control mechanism to achieve: i) the magnitude of the centrifugal force generated by the first mass center offset wheel (3a) is equal to the magnitude of the centrifugal force generated by the second mass center offset wheel (3b); ii) the horizontal component of the centrifugal force generated by the first mass-center offset wheel (3a) and the horizontal component of the centrifugal force generated by the second mass-center offset wheel (3b) completely cancel each other out on the support mechanism; iii) The vertical component of the centrifugal force generated by the first mass center offset wheel (3a) and the vertical component of the centrifugal force generated by the second mass center offset wheel (3b) are superimposed on each other on the support mechanism to form a vertical control force, and the relationship between the vertical control force and time can be expressed by the following sine function: F 0 =2×F S ×sin(ωt±θ) ,in, F 0 is the vertical control force, F S is the centrifugal force generated by the first mass-center offset wheel (3a) or the centrifugal force generated by the second mass-center offset wheel (3b), ω is the rotational angular velocity of the first mass-center offset wheel (3a) or the rotational angular velocity of the second mass-center offset wheel (3b), t Indicates time, θ It represents the rotation phase of the center of mass of the first eccentric mass (4a) or the rotation phase of the center of mass of the second eccentric mass (4b).

3. A double eccentric inertial actuator for targeted vibration reduction of a railway vehicle bogie as claimed in claim 2, characterized in that: When the device is used, the double eccentric vibration frequency phase control mechanism controls the set speed so that the sine function F 0 The changing frequency is consistent with the dominant mode resonance frequency of the bogie frame (12) and F 0 The instantaneous phase of is opposite to the instantaneous phase of the dominant mode resonance of the bogie frame (12).

4. A double eccentric wheel inertial actuator for targeted vibration reduction of a railway vehicle bogie as claimed in claim 3, characterized in that: When the device is used, the set speed is controlled by the double eccentric vibration frequency phase control mechanism so that the sine function F 0 The changing frequency is consistent with the dominant mode resonance frequency of the bogie frame (12) and F 0 After the instantaneous phase of the bogie frame (12) is opposite to the instantaneous phase of the dominant mode resonance, the set center of mass offset is adjusted through the double eccentric wheel vibration amplitude control mechanism so that the magnitude of the vertical control force reaches a level that can technically effectively suppress the vertical vibration of the bogie frame (12).

5. A double eccentric inertial actuator for targeted vibration reduction of a railway vehicle bogie according to any one of claims 1 to 4, characterized in that: The double eccentric wheel vibration frequency phase control mechanism comprises a driving motor (1) and a driving gear set (2), wherein the driving gear set (2) comprises a first driving gear (2a) and a second driving gear (2b), wherein the first driving gear (2a) is connected to the output shaft of the driving motor (1), the second driving gear (2b) and the first driving gear (2a) have the same number of teeth and mesh with each other, the first mass center offset wheel (3a) is coaxially fixedly connected to the first driving gear (2a) to form a first rotating assembly, the second mass center offset wheel (3b) is coaxially fixedly connected to the second driving gear (2b) to form a second rotating assembly, and the first rotating assembly and the second rotating assembly are rotatably supported on a supporting mechanism.

6. A double eccentric inertial actuator for targeted vibration reduction of a railway vehicle bogie as claimed in claim 5, characterized in that: The driving motor (1) is a servo motor.

7. A double eccentric inertial actuator for targeted vibration reduction of a railway vehicle bogie according to any one of claims 1 to 4, characterized in that: The first mass center offset wheel (3a) has a first mass center offset wheel body, a first screw mechanism (5a) is provided on the first mass center offset wheel body, a first eccentric mass (4a) is installed on the first screw mechanism (5a) as a nut capable of linear reciprocating motion in the first screw mechanism (5a), and the second mass center offset wheel (3b) has a second mass center offset wheel body, a second screw mechanism (5b) is provided on the second mass center offset wheel body, and a second eccentric mass (4b) is installed on the second screw mechanism (5b) as a nut capable of linear reciprocating motion in the second screw mechanism (5b); the double eccentric wheel vibration amplitude control mechanism controls the first mass center offset amount by controlling the rotation of the screw in the first screw mechanism (5a), and controls the second mass center offset amount by controlling the rotation of the screw in the second screw mechanism (5b).

8. A double eccentric inertial actuator for targeted vibration reduction of a railway vehicle bogie as claimed in claim 7, characterized in that: The double eccentric wheel vibration amplitude control mechanism comprises an amplitude modulation motor group (6), the amplitude modulation motor group (6) comprises a first amplitude modulation motor (6a) and a second amplitude modulation motor (6b), the first amplitude modulation motor (6a) is transmission-connected to a first screw mechanism (5a), and the second amplitude modulation motor group (6b) is transmission-connected to a second screw mechanism (5b).

9. A double eccentric wheel inertial actuator for targeted vibration reduction of a railway vehicle bogie as claimed in claim 8, characterized in that: The first amplitude modulation motor (6a) is coaxially arranged with the rotation center of the first mass center offset wheel (3a), and the first amplitude modulation motor (6a) is transmission-connected to the first screw mechanism (5a) via a first bevel gear transmission mechanism; the second amplitude modulation motor (6b) is coaxially arranged with the rotation center of the second mass center offset wheel (3b), and the second amplitude modulation motor (6b) is transmission-connected to the second screw mechanism (5b) via a second bevel gear transmission mechanism.

10. A double eccentric inertial actuator for targeted vibration reduction of a railway vehicle bogie as claimed in claim 9, characterized in that: The double eccentric wheel vibration amplitude control mechanism comprises two collector rings (7), each of the two collector rings (7) comprises a fixed part and a rotating part, the fixed parts of the two collector rings (7) are used to be connected to an external power source, the rotating part of one collector ring (7) rotates along with the rotation of a first amplitude modulation motor (6a) to supply power to the first amplitude modulation motor (6a), and the rotating part of one collector ring (7) rotates along with the rotation of a second amplitude modulation motor (6b) to supply power to the second amplitude modulation motor (6b).

Images