A vibration reduction method for a magnetic guideway absorber

Abstract

The application discloses a damping method of a magnetic guide rail vibration absorber, the vibration absorber comprising a support and two mutually perpendicular and fixedly connected magnetic guide rails, the bottom of the support being fixed on a motor, the upper end of the support being fixedly connected with the connecting nodes of the two magnetic guide rails, the magnetic guide rails being supported, the end of each magnetic guide rail being slidably connected with a mass block, a spring being connected between each mass block and the connecting node of the two magnetic guide rails, the spring being wound on the magnetic guide rail, the mass block being a coil wound with the magnetic guide rail as a central axis, and the two ends of the coil being connected with an electric resistor R through wires; the application has the advantages that the energy generated by vibration is consumed in the electric resistor R, thereby reducing the vibration energy of the motor and achieving a better damping effect.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of vibration reduction of vertical rotating equipment, and more particularly to a vibration reduction method of a magnetic guide rail vibration absorber. BACKGROUND

[0002] At present, in the industrial production process, in view of energy saving, some large motors are often transformed by frequency conversion. For vertical motors, the horizontal support stiffness is weak, the shaft system is long, and the critical speed is generally lower than the operating speed. This causes the operating speed of the equipment to often fall within the critical speed range after the vertical motor is transformed by frequency conversion, resulting in excessive vibration of the upper part of the motor.

[0003] There are two common methods to deal with critical vibration: one is to reduce the unbalance of the shaft system by dynamic balancing to reduce the unbalance excitation force of the shaft system, thereby reducing the unbalance vibration response at the critical speed. This method can reduce the vibration amplitude at the critical speed to a certain extent, but it requires high balancing accuracy to control the shaft vibration amplitude at the critical speed within the qualified range. The second method is to strengthen the fixed support strength of the upper part of the motor to suppress the vibration response at the critical speed. The hard support method of top wire is generally used in the field. However, it is difficult to control the support strength of each point to be consistent, and in the case of poor control, it may cause the center line of the shaft system to be inconsistent, which not only cannot achieve the effect of reducing vibration, but also aggravates the vibration. At the same time, when the vibration is too large, the rigid support may also cause damage to the equipment.

[0004] Chinese patent publication No. CN203670596U discloses a simply supported beam type frequency adjustable dynamic vibration absorber, which comprises a base, a stepping motor, a sliding block, a transmission screw, and a metal beam. The base has a dovetail groove, the lower end of the sliding block is in dovetail shape, the upper end of the sliding block is a support arm with a hole, and the middle part of the sliding block is a threaded hole. The sliding block has two, the lower ends of the two sliding blocks are installed in the dovetail groove, the middle part of the metal beam has a concentrated mass block, the two ends of the metal beam pass through the holes of the support arms of the upper ends of the two sliding blocks, the outer wall of the transmission screw is symmetrically provided with reverse threads, the transmission screw passes through the threaded holes of the two sliding blocks and cooperates with the threads of the two threaded holes, and the first end of the transmission screw is connected with the stepping motor. Compared with the cantilever type vibration absorber, the requirement for outward extension space is reduced. However, the structure of the vibration absorber itself is complex, and there are many devices, which may cause the vibration absorber to become a new vibration source and reduce the vibration reduction effect. SUMMARY

[0005] The technical problem to be solved by the present application is the poor vibration reduction effect of the vibration absorber of the prior art vertical rotating equipment.

[0006] The application solves the above technical problems by the following technical means: a magnetic guide rail vibration absorber, comprising a support and two mutually perpendicular and fixedly connected magnetic guide rails, the bottom of the support being fixed on a motor, the upper end of the support being fixedly connected with the connecting nodes of the two magnetic guide rails to support the magnetic guide rails, the end of each guide rail being slidably connected with a mass block, each mass block being connected with a spring between the connecting nodes of the two magnetic guide rails, the mass block being a coil wound around the magnetic guide rail as a central axis, and the two ends of the coil being connected with a resistor R through a wire.

[0007] Under the action of the vibration absorber, the mass block composed of the coil synchronously performs simple harmonic vibration on the magnetic guide rail, according to the principle of electromagnetic induction, the coil cuts the magnetic induction lines to generate an induced electromotive force, the coil is connected in series with the resistor R, the vibration energy of the mass block is converted into the heat of the resistor R, the energy generated by vibration is consumed in the resistor R, thereby reducing the vibration energy of the motor and achieving a better vibration reduction effect.

[0008] Further, the spring is a spring damper.

[0009] Further, the support comprises four equal-length support legs, one end of each support leg being fixed on the motor, the other end of each support leg being connected together and fixedly connected with the connecting nodes of the two magnetic guide rails, and the one ends of the four support legs surrounding a rectangle.

[0010] Further, the motor is a motor of a vertical rotating device.

[0011] The application further provides a vibration reduction method of a magnetic guide rail vibration absorber, the method comprising:

[0012] Step one: obtaining a vibration equation of a two-degree-of-freedom double-damping vibration system under the action of an exciting force of a motor;

[0013] Step two: obtaining a complex equation of forced vibration in a stable state and solving the complex equation, and obtaining a force of the mass block acting on the upper surface of the motor according to the solution of the complex equation;

[0014] Step three: selecting parameters of the vibration absorber so that the vibration is absorbed;

[0015] Step four: adjusting an amplification factor so that the displacement of the motor under the action of the exciting force is minimum in a full frequency band, i.e., the complex solution of the vibration of the single-degree-of-freedom vibration system in the stable state is minimum, and obtaining an optimal damping ratio of the vibration absorber and an optimal natural frequency of the vibration absorber.

[0016] Further, the step one comprises:

[0017] using the formula The vibration equation of a two-degree-of-freedom double-damping vibration system under the action of the exciting force of the motor is obtained; wherein, M represents the mass of the motor, m represents the mass of the mass block, K represents the elastic coefficient of the motor, k represents the elastic coefficient of the mass block, C1 represents the damping coefficient of the motor, C2 represents the damping coefficient of the mass block, x1 represents the displacement of the motor, x2 represents the displacement of the mass block, and P(t) represents the exciting force.

[0018] Further, the step two comprises:

[0019] If the exciting force of the motor is a simple harmonic force, the vibration equation of the two-degree-of-freedom double-damping vibration system is transformed to obtain the complex equation of forced vibration in the stable state as

[0020]

[0021] wherein, ω represents the exciting frequency, i represents the complex imaginary unit, X1 represents the complex variable of the displacement of the motor, X2 represents the complex variable of the displacement of the mass block, and P represents the complex variable of the exciting force.

[0022] The complex equation is solved to obtain

[0023]

[0024] The force of the mass block acting on the upper surface of the motor is obtained by the formula

[0025] Further, the step three comprises:

[0026] The complex solution of the single-degree-of-freedom vibration system in the stable state is obtained by the formula X 10 = P / (K-Mω 2 +iωC1);

[0027] The force of the motor itself is obtained by the formula F 10 =(K+iωC1)P / (K-Mω 2 +iωC1), wherein F 10 represents the force of the motor itself.

[0028] The relationship between the vibration absorption performance and the exciting force frequency is obtained by the formula wherein, ξ represents the vibration absorption coefficient, E1 represents the vibration energy of the mass block acting on the motor, and E 10 represents the vibration energy of the motor itself, V1 represents the complex variable of the vibration speed of the mass block acting on the motor, and V 10 represents the complex variable of the vibration speed of the motor itself.

[0029] ​​The strongest frequency of the complex variable of the motor's own vibration speed is obtained by the formula The parameters of the vibration absorber are selected so that ξ>0, wherein ω r is the strongest frequency of the complex variable of the motor's own vibration speed.

[0030] Further, the step four comprises:

[0031] Let wherein β represents an amplification factor and

[0032]

[0033] wherein ω n represents the natural frequency of the motor, μ represents the ratio of the mass of the mass block to the mass of the motor, ω0 represents the natural frequency of the vibration absorber, ζ1 represents the damping ratio of the motor, and ζ2 represents the damping ratio of the vibration absorber, and

[0034] The amplification factor is adjusted so that the displacement of the motor under the action of the exciting force is minimized in the full frequency band, i.e., the complex solution of the single-degree-of-freedom vibration system in the stable state is minimized.

[0035] Further, the process of adjusting the amplification factor comprises:

[0036] Step 401: taking a frequency band γ a ≤ω1≤γ b in the neighborhood of the natural frequency of the motor, wherein γ a =0.7ω n , γ b =1.3ω n ;

[0037] Step 402: substituting the initial value of the natural frequency of the vibration absorber and the initial value of the damping ratio of the vibration absorber into the calculation formula of the amplification factor to calculate the value of the amplification factor in the frequency band;

[0038] Step 403: updating the natural frequency of the vibration absorber and the damping ratio of the vibration absorber, taking the updated natural frequency of the vibration absorber as the initial value of the natural frequency of the vibration absorber, taking the updated damping ratio of the vibration absorber as the initial value of the damping ratio of the vibration absorber, returning to execute step 402 until the minimum value of the amplification factor is obtained, taking the damping ratio of the vibration absorber at this time as the optimal damping ratio of the vibration absorber, and taking the natural frequency of the vibration absorber at this time as the optimal natural frequency of the vibration absorber.

[0039] The present application has the following advantages:

[0040] (1) The mass block composed of the coil synchronously performs simple harmonic vibration on the magnetic guide rail under the action of the vibration absorber, according to the principle of electromagnetic induction, the coil cuts the magnetic induction lines to generate an induced electromotive force, the coil is connected in series with the resistance R, the vibration energy of the mass block is absorbed from the motor and converted into the heat of the resistance R, the energy generated by the vibration is consumed in the resistance R, thereby reducing the vibration energy of the motor, and a better vibration reduction effect is achieved.

[0041] (2) The parameters of the vibration absorber are selected so that the vibration is absorbed, the amplification factor is adjusted so that the displacement of the motor under the action of the excitation force is minimum in the full frequency band, the optimal damping ratio of the vibration absorber and the optimal natural frequency of the vibration absorber are obtained, the vibration reduction effect is analyzed and calculated, and the vibration reduction effect is optimal. BRIEF DESCRIPTION OF DRAWINGS

[0042] Figure 1 A front view of a magnetic guide rail vibration absorber provided by the embodiment of the present application;

[0043] Figure 2 A top view of a magnetic guide rail vibration absorber provided by the embodiment of the present application;

[0044] Figure 3 A connection diagram of the coil in the mass block and the resistance R in a magnetic guide rail vibration absorber provided by the embodiment of the present application;

[0045] Figure 4 A physical model of a single-degree-of-freedom single-damping vibration system in a magnetic guide rail vibration absorber provided by the embodiment of the present application;

[0046] Figure 5 A physical model of a two-degree-of-freedom double-damping vibration system in a magnetic guide rail vibration absorber provided by the embodiment of the present application;

[0047] Figure 6 A flowchart of a vibration reduction method of a magnetic guide rail vibration absorber provided by the embodiment of the present application. DETAILED DESCRIPTION

[0048] To make the purpose, technical scheme and advantages of the embodiment of the present application clearer, the technical scheme in the embodiment of the present application will be described clearly and completely below in combination with the embodiment of the present application. Obviously, the described embodiment is a part of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiment in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0049] As shown in Figures 1 to 3 A magnetic guide rail vibration absorber, comprising a support 4 and two mutually perpendicular and fixedly connected magnetic guide rails 2.

[0050] The support 4 comprises four equal-length support legs, one end of each support leg is fixed on the motor 5, and the motor 5 is a motor of the vertical rotating device. The other end of each support leg is connected together and fixedly connected with the connecting nodes of the two magnetic guide rails 2, and the one end of the four support legs forms a rectangle.

[0051] The upper end of the support 4 is fixedly connected with the connecting nodes of the two magnetic guide rails 2, and the magnetic guide rails 2 are supported. The two magnetic guide rails 2 are perpendicular to each other, correspond to the working medium flow direction of the vertical motor 5 and the vertical working medium flow direction respectively, and the two groups of fin-shaped vibration absorbers can be adjusted in frequency parameter and correspond to different vibration frequencies in two directions respectively, so that the vibration reduction effect is improved.

[0052] The end of each magnetic guide rail 2 is slidably connected with a mass block 1, and the weight of the mass block 1 can be adjusted by replacement, so that the frequency width of the damping is improved.

[0053] Each mass block 1 is connected with the connecting nodes of the two magnetic guide rails 2, and a spring 3 is arranged between the connecting nodes of the two magnetic guide rails 2. The spring 3 is a spring damper. The spring 3 is wound on the magnetic guide rail 2, the mass block 1 is a coil wound on the magnetic guide rail as a center axis, and the two ends of the coil are connected with a resistor R (not shown in the figure) through a wire.

[0054] Continuing to refer to Figures 1 to 3 , the vibration absorbers are arranged according to the working medium flow direction (X direction) of the motor 5 and the vertical working medium flow direction (Y direction). When the motor 5 has a larger vibration, the X direction vibration causes the vibration absorber group composed of the mass block C, the mass block D and the spring damper to vibrate. According to the related parameters of the main system with the motor 5 as the main body, the elastic coefficient of the mass block C, the mass block D and the spring damper is designed to be appropriate, so that the attached vibration absorber system can absorb part of the X direction vibration energy of the main system, and the X direction vibration amplitude can be reduced.

[0055] Similarly, the vibration absorber group composed of the mass block A, the mass block B and the spring damper can absorb the Y direction vibration energy and reduce the Y direction vibration amplitude.

[0056] In the plane composed of the mutually perpendicular X and Y directions, the vibration in each direction can be decomposed into the synthesis of the X and Y direction vibrations, so that under the action of the X and Y direction vibration absorbers, the vibration amplitude in each direction of the horizontal plane can be reduced.

[0057] Under the action of the vibration absorber, the mass block 1 composed of the coil performs synchronous simple harmonic vibration on the magnetic guide rail 2. According to the principle of electromagnetic induction, the coil cuts the magnetic induction lines to generate an induced electromotive force. The coil is connected in series with the resistor R, the vibration energy of the mass block 1 is absorbed from the motor 5 and converted into the heat of the resistor R, the vibration energy is consumed in the resistor R, so that the vibration energy of the motor is reduced, and a good vibration reduction effect is achieved.

[0058] Neglecting the influence of some secondary factors, the motor 5 can be simplified as Figure 4 The physical model shown contains a single-degree-of-freedom single-damping vibration system, and if an absorber composed of k-m-C2 is added, it becomes Figure 5 The two-degree-of-freedom double-damping vibration system shown, as Figure 6 The application also provides a vibration reduction method of a magnetic guide rail absorber, and the method comprises the following steps:

[0059] Step S1: obtaining a vibration equation of a two-degree-of-freedom double-damping vibration system under the action of an exciting force of the motor 5; the specific process is as follows:

[0060] The formula is used to obtain the vibration equation of the two-degree-of-freedom double-damping vibration system under the action of the exciting force of the motor 5 (not taking gravity and initial displacement into account); wherein M represents the mass of the motor 5, m represents the mass of the mass block 1, K represents the elastic coefficient of the motor 5, k represents the elastic coefficient of the mass block 1, C1 represents the damping coefficient of the motor 5, C2 represents the damping coefficient of the mass block 1, x1 represents the displacement of the motor 5, x2 represents the displacement of the mass block 1, and P(t) represents the exciting force.

[0061] Step S2: obtaining a complex equation of forced vibration in a stable state and solving the complex equation, and obtaining the force of the mass block 1 acting on the upper surface of the motor 5 according to the solution of the complex equation; the specific process is as follows:

[0062] The exciting force P(t) of mechanical vibration is usually a periodic external force. If the exciting force of the motor 5 is a simple harmonic force, the complex equation of forced vibration in a stable state is obtained by transforming the vibration equation of the two-degree-of-freedom double-damping vibration system, and the complex equation is

[0063]

[0064] Wherein ω represents the exciting frequency, i represents the complex imaginary unit, X1 represents the complex variable of the displacement of the motor 5, X2 represents the complex variable of the displacement of the mass block 1, and P represents the complex variable of the exciting force. The solution of the complex equation is

[0065]

[0066] The force of the mass block 1 acting on the upper surface of the motor 5 is obtained by the formula , wherein F1 represents the force of the mass block 1 acting on the upper surface of the motor 5.

[0067] Step S3: selecting the parameters of the absorber so that the vibration is absorbed; the specific process is as follows:

[0068] The formula X 10 =P / (K-Mω 2+ iωC1), get the complex solution of the single degree of freedom vibration system in the steady state vibration;

[0069] Through the formula F 10 = (K + iωC1) P / (K - Mω 2 + iωC1), get the force of the motor 5 itself, wherein, F 10 represents the force of the motor 5 itself; equivalent to Figure 5 The case of m = 0, C2 = 0 in the system.

[0070] Under the same excitation force, whether the vibration absorber composed of k ~ m ~ C2 is attached, the vibration energy E1 of the motor 5 and the force F1 acting on the upper surface of the motor 5 are usually different, and the change has a direct relationship with the frequency of the excitation force. The relationship between the vibration absorption performance and the frequency of the excitation force (i.e. the frequency characteristic of the vibration absorption) is analyzed in detail below.

[0071] Through the formula get the relationship between the vibration absorption performance and the frequency of the excitation force, wherein, ξ represents the vibration absorption coefficient, E1 represents the vibration energy of the mass block 1 acting on the motor 5, E 10 represents the vibration energy of the motor 5 itself, V1 represents the complex variable of the vibration speed of the mass block 1 acting on the motor 5, V 10 represents the complex variable of the vibration speed of the motor 5 itself;

[0072] Obviously, ξ > -1, when ξ > 0, F 10 / F1 (or E 10 / E1) > 1, indicating that after the vibration absorber is attached, the vibration of the K ~ M ~ C1 damping vibration system is "absorbed"; when -1 < ξ < 0, F 10 / F1 (or E 10 / E1) < 1, indicating that after the damping vibration absorber is attached, the vibration of the K ~ M ~ C1 damping vibration system is enhanced; when ξ = 0, F 10 / F1 (or E 10 / E1) = 1, indicating that the damping vibration absorber has no effect on the K ~ M ~ C1 vibration system.

[0073] Therefore, the principle of designing the vibration absorber is to select appropriate k, m, C2 parameters to make ξ > 0.

[0074] When the mechanical system is running, the frequency spectrum of its vibration (such as vibration speed V 10 ) can be measured, then the vibration absorber k ~ m ~ C2 can be attached to the mechanical system, and the parameters k, m, C2 are appropriately selected, so that the interval (ω min , ω max ) contains V 10The frequency of the strong vibration is ω

[0075] In V 10 The frequency of the strong vibration is ω r The parameters k, m, C2 of the vibration absorber are selected so that ω r is located between the damping natural frequency ω and the natural frequency ω , i.e.:

[0076]

[0077] Then:

[0078]

[0079] The vibration component of the mechanical system at the frequency ω r is greatly weakened, and the vibration energy in a large frequency range on both sides of ω r is attenuated to different degrees, so that the total vibration is weakened.

[0080] When selecting the parameters of the vibration absorber, the larger the values of k, m, C2, the larger the frequency range (ω min , ω max ) of the vibration absorption, and the better the vibration absorption effect. However, when k, m, C2 are too large, the vibration absorber may be difficult to arrange on the mechanical system, and the vibration absorber itself becomes a new vibration source. Therefore, m≤M, k≤K should be generally satisfied, and the values of k, m, C2 should be appropriately adjusted to be in the optimal vibration absorption state.

[0081] Step S4: Adjust the amplification factor to minimize the displacement of the motor 5 under the action of the excitation force in the full frequency band, i.e. the complex solution of the vibration of the single-degree-of-freedom vibration system in the steady state is minimized, and the optimal damping ratio of the vibration absorber and the optimal natural frequency of the vibration absorber are obtained. The specific process is as follows:

[0082] Let where β represents the amplification factor and

[0083]

[0084] where ω n represents the natural frequency of the motor 5, μ represents the mass ratio of the mass block 1 to the motor 5, ω0 represents the natural frequency of the vibration absorber, ζ1 represents the damping ratio of the motor 5, and ζ2 represents the damping ratio of the vibration absorber, and

[0085] Adjusting the amplification factor to minimize the displacement of the motor 5 under the exciting force in the whole frequency band, i.e. the complex solution of the single-degree-of-freedom vibration system in the stable state.

[0086] The adjusting process of the amplification factor is as follows:

[0087] Step 401: Taking a frequency band γ in the neighborhood of the natural frequency of the motor 5 a ≤ω1≤γ b , wherein γ a =0.7ω n , γ b =1.3ω n ;

[0088] Step 402: Substituting the initial value of the natural frequency of the vibration absorber and the initial value of the damping ratio of the vibration absorber into the calculation formula of the amplification factor to calculate the value of the amplification factor in the frequency band;

[0089] Step 403: Updating the natural frequency of the vibration absorber and the damping ratio of the vibration absorber, taking the updated natural frequency of the vibration absorber as the initial value of the natural frequency of the vibration absorber, taking the updated damping ratio of the vibration absorber as the initial value of the damping ratio of the vibration absorber, returning to Step 402 until the minimum value of the amplification factor is obtained, taking the damping ratio of the vibration absorber at this time as the optimal damping ratio of the vibration absorber, and taking the natural frequency of the vibration absorber at this time as the optimal natural frequency of the vibration absorber.

[0090] The above embodiments are only used to illustrate the technical solutions of the present application, but not to limit it; although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that they can still modify the technical solutions recorded in the foregoing embodiments, or make equivalent replacement to part of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the embodiments of the present application.

Claims

1. A vibration reduction method for a magnetic guide rail vibration absorber, characterized in that: The magnetic guide rail vibration absorber includes a bracket and two mutually perpendicular and fixedly connected magnetic guide rails, the bottom of the bracket is fixed to the motor, the upper end of the bracket is fixedly connected to the connection node of the two magnetic guide rails, and supports the magnetic guide rails. The end of each magnetic guide rail is slidably connected to a mass block, and a spring is connected between each mass block and the connection node of the two magnetic guide rails. The spring is wound on the magnetic guide rail, and the mass block is a coil wound around the magnetic guide rail as the central axis, and the two ends of the coil are connected to a resistor R through a wire. The method includes: Step 1: Obtaining a vibration equation of a two-degree-of-freedom double-damped vibration system under the excitation force of the motor; Step 1 includes: Using the formula Obtain the vibration equation of the two-degree-of-freedom double-damped vibration system under the excitation force of the motor; where M represents the mass of the motor, m represents the mass of the mass block, K represents the elastic coefficient of the motor, k represents the elastic coefficient of the mass block, C1 represents the damping coefficient of the motor, C2 represents the damping coefficient of the mass block, x1 represents the displacement of the motor, x2 represents the displacement of the mass block, and P(t) represents the excitation force; Step 2: Obtain a complex equation of forced vibration in a stable state and solve the complex equation, and obtain the force of the mass block acting on the upper surface of the motor according to the solution of the complex equation; Step 2 includes: If the exciting force of the motor is a simple harmonic force, the vibration equation of the two-degree-of-freedom double-damped vibration system is transformed to obtain the complex equation of forced vibration in the stable state: Where ω represents the excitation frequency, i represents the complex imaginary unit, X1 represents the complex variable of the motor displacement, X2 represents the complex variable of the displacement of the mass block, and P represents the complex variable of the excitation force. Solving the complex equation yields By formula Obtain the force exerted by the mass block on the upper surface of the motor, where F1 represents the force exerted by the mass block on the upper surface of the motor; Step 3: Select the parameters of the vibration absorber so that the vibration is absorbed; By formula X 10 =P / (K-Mω 2 +iωC1) obtain the complex solution of the single-degree-of-freedom vibration system in a stable state; By formula F 10 =(K+iωC1)P / (K-Mω 2 +iωC1) to obtain the force of the motor itself, where F 10 Indicates the force of the motor itself; By formula Obtain the relationship between vibration absorption performance and exciting force frequency, where, ξ represents the vibration absorption coefficient, E1 represents the vibration energy after the mass block acts on the motor, and E 10 Indicates the vibration energy of the motor itself; Using the strongest frequency of the complex variable of the motor's vibration speed, the formula The parameters of the vibration absorber are selected so that ξ>0, where ω r is the strongest frequency of the complex variable of the motor's vibration speed; Step 4: Adjust the amplification factor so that the displacement of the motor under the action of the exciting force is minimized in the entire frequency band, that is, the complex solution of the vibration of the single-degree-of-freedom vibration system in the stable state is minimized, and the optimal damping ratio and the optimal natural frequency of the vibration absorber are obtained.

2. The vibration reduction method of a magnetic guide rail vibration absorber according to claim 1, characterized in that: The spring is a spring damper.

3. The vibration reduction method of a magnetic guide rail vibration absorber according to claim 1, characterized in that: The bracket includes four supporting legs of equal length, one end of each supporting leg is fixed on the motor, the other end of each supporting leg is connected together and fixedly connected to the connection nodes of the two magnetic guide rails, and one end of the four supporting legs forms a rectangle.

4. The vibration reduction method of a magnetic guide rail vibration absorber according to claim 1, characterized in that: The motor is a motor of a vertical rotating device.

5. The vibration reduction method of a magnetic guide rail vibration absorber according to claim 1, characterized in that: The fourth step includes: make where β represents the amplification factor and Among them, ω n represents the natural frequency of the motor, μ represents the ratio of the mass block to the motor mass, ω0 represents the natural frequency of the vibration absorber, ζ1 represents the damping ratio of the motor and ζ2 represents the damping ratio of the vibration absorber and The amplification factor is adjusted so that the displacement of the motor under the action of the exciting force is minimized in the entire frequency band, that is, the complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state is minimized.

6. The vibration reduction method of a magnetic guide rail vibration absorber according to claim 5, characterized in that: The process of adjusting the amplification factor is as follows: Step 401: Take a frequency band γ in the neighborhood of the natural frequency of the motor a ≤ω1≤γ b , where γ a =0.7ω n , γ b =1.3ω n ; Step 402: Substitute the initial value of the natural frequency of the vibration absorber and the initial value of the damping ratio of the vibration absorber into the calculation formula of the amplification factor to calculate the value of the amplification factor within the frequency band; Step 403: Update the natural frequency and damping ratio of the vibration absorber, use the updated natural frequency of the vibration absorber as the initial value of the natural frequency of the vibration absorber, and use the updated damping ratio of the vibration absorber as the initial value of the damping ratio of the vibration absorber, and return to execute step 402 until the minimum value of the amplification factor is obtained, and use the damping ratio of the vibration absorber at this time as the optimal damping ratio of the vibration absorber, and the natural frequency of the vibration absorber at this time as the optimal natural frequency of the vibration absorber.

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