阅读说明：本技术 一种磁性导轨吸振器及其减振方法 (Magnetic guide rail vibration absorber and vibration reduction method thereof ) 是由 陈悦 李敬豪 庞靖 袁昊 邢海波 阮圣奇 吴仲 肖宇煊 陈开峰 邵飞 朱涛 宋 于 2020-08-10 设计创作，主要内容包括：本发明公开了一种磁性导轨吸振器及其减振方法,吸振器包括支架和两个相互垂直且固定连接的磁性导轨,所述支架底部固定在电机上,支架上端与两个磁性导轨的连接节点固定连接,支撑所述磁性导轨,每个磁性导轨的端部均滑动连接一个质量块,每个所述质量块与两个磁性导轨的连接节点之间均连接有一个弹簧,弹簧缠绕在磁性导轨上,质量块为以磁性导轨为中心轴缠绕的线圈,线圈的两端通过导线连接一个电阻R；本发明的优点在于：将振动产生的能量在电阻R中消耗,从而降低电机的振动能量,实现较好的减振效果。(The invention discloses a magnetic guide rail vibration absorber and a vibration damping method thereof, wherein the vibration absorber comprises a bracket and two magnetic guide rails which are vertical to each other and are fixedly connected, the bottom of the bracket is fixed on a motor, the upper end of the bracket is fixedly connected with a connecting node of the two magnetic guide rails to support the magnetic guide rails, the end part of each magnetic guide rail is slidably connected with a mass block, a spring is connected between each mass block and the connecting node of the two magnetic guide rails, the spring is wound on the magnetic guide rails, the mass block is a coil wound by taking the magnetic guide rails as a central shaft, and the two ends of the coil are connected with a resistor R through leads; the invention has the advantages that: the energy generated by vibration is consumed in the resistor R, so that the vibration energy of the motor is reduced, and a good vibration reduction effect is realized.)

1. The utility model provides a magnetism guide rail bump leveller which characterized in that, includes support and two mutually perpendicular and fixed connection's magnetism guide rail, the support bottom is fixed on the motor, and the support upper end is connected with the connected node fixed connection of two magnetism guide rails, supports the magnetism guide rail, the equal sliding connection mass block of tip of every magnetism guide rail, every all be connected with a spring between the connected node of mass block and two magnetism guide rails, the spring winding is on the magnetism guide rail, and the mass block is for using magnetism guide rail as the winding coil of center pin, and a resistance R is passed through the wire at the both ends of coil.

2. The magnetic rail vibration absorber of claim 1 wherein said spring is a spring damper.

3. The magnetic guide rail vibration absorber according to claim 1 wherein the bracket comprises four equal length support legs, one end of each support leg is fixed to the motor, the other end of each support leg is connected together and fixedly connected to the connection node of the two magnetic guide rails, and one end of each of the four support legs is enclosed into a rectangle.

4. The magnetic rail vibration absorber of claim 1 wherein said motor is a motor of a vertical rotating apparatus.

5. The method for damping vibration of a magnetic rail vibration absorber according to any one of claims 1 to 4, wherein the method comprises:

the method comprises the following steps: acquiring a vibration equation of a two-degree-of-freedom double-damping vibration system under the action of an excitation force of a motor;

step two: acquiring a complex equation of forced vibration in a stable state, solving the complex equation, and acquiring the force of a mass block acting on the upper surface of the motor according to the solution of the complex equation;

step three: selecting parameters of the vibration absorber to enable vibration to be absorbed;

step four: and adjusting the amplification factor to minimize the displacement of the motor under the action of the exciting force on a full frequency band, namely minimizing a complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state, and acquiring the damping ratio of the optimal vibration absorber and the natural frequency of the optimal vibration absorber.

6. The vibration reduction method of the magnetic rail vibration absorber according to claim 5, wherein the first step comprises:

using formulasAcquiring a vibration equation of a two-degree-of-freedom double-damping vibration system under the action of an excitation force of a motor; 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, C₁Representing the damping coefficient of the motor, C₂Representing the damping coefficient, x, of the mass₁Representing the displacement of the motor, x₂Represents the displacement of the mass, and p (t) represents the excitation force.

7. The vibration reduction method of the magnetic guide rail vibration absorber according to claim 5, wherein the second step comprises:

if the exciting force of the motor is simple harmonic force, the vibration equation of the two-freedom double-damping vibration system is transformed, and the complex equation of the forced vibration in a stable state is obtained as

Where ω denotes the excitation frequency, i denotes the complex imaginary unit, X₁A complex variable, X, representing the displacement of the motor₂Expressing the complex variable of the displacement of the mass block, P expressing the complex variable of the exciting force, and solving the complex equation to obtain

By the formula

8. The vibration reduction method of the magnetic guide rail vibration absorber according to claim 5, wherein the third step comprises:

by the formula X₁₀＝P/(K-Mω²+iωC₁) Obtaining a complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state;

by the formula F₁₀＝(K+iωC₁)P/(K-Mω²+iωC₁) Obtaining the force of the motor itself, wherein F₁₀Representing the force of the motor itself;

by the formulaObtaining a relation between the vibration absorption performance and the frequency of the exciting force, wherein,xi represents the vibration absorption coefficient, E₁Representing the vibration energy of the mass after acting on the motor, E₁₀Representing the vibration energy of the motor itself, V₁A complex variable, V, representing the speed of vibration of the mass after it has acted on the motor₁₀A complex variable representing the vibration speed of the motor itself;

by means of the strongest frequency equation of complex variable of vibration speed of motorSelecting parameters of the vibration absorber to make xi>0, wherein ω_rThe strongest frequency of the complex variable of the vibration speed of the motor itself.

9. The vibration damping method for a magnetic guide rail vibration absorber according to claim 5, wherein said step four comprises:

order to

wherein, ω is_nRepresenting the natural frequency of the motor, mu representing the ratio of the mass to the mass of the motor, omega₀Showing the natural frequency, ζ, of the vibration absorber₁Represents the damping ratio of the motor andζ₂represents the damping ratio of the vibration absorber and

the amplification factor is adjusted to ensure that the displacement of the motor under the action of the exciting force is minimum in a full frequency band, namely the complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state is minimum.

10. The vibration damping method for the magnetic rail vibration absorber according to claim 9, wherein the process of adjusting the amplification factor comprises:

step 401: taking a frequency band gamma in the neighborhood of the natural frequency of the motor_a≤ω₁≤γ_bWherein γ is_a＝0.7ω_n，γ_b＝1.3ω_n；

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 a calculation formula of the amplification factor to calculate the value of the amplification factor in the frequency band;

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 the step 402 until the minimum value of the amplification factor is obtained, taking the damping ratio of the vibration absorber at the moment as the damping ratio of the optimal vibration absorber, and taking the natural frequency of the vibration absorber at the moment as the natural frequency of the optimal vibration absorber.

Technical Field

The invention relates to the technical field of vibration reduction of vertical rotating equipment, in particular to a magnetic guide rail vibration absorber and a vibration reduction method thereof.

Background

In the industrial production process, in order to save energy, frequency conversion transformation is often carried out on some large motors, and for vertical motors, the horizontal support rigidity is weak; the shaft system is long, and the critical rotating speed is generally lower than the power frequency running rotating speed. After the frequency conversion transformation of the vertical motor, the running rotating speed of the equipment often falls in the critical rotating speed range, and the vibration of the upper part of the motor exceeds the standard.

There are two common methods of dealing with critical vibrations currently used: one method is to reduce the unbalance amount of the shafting in a dynamic balance mode and reduce the unbalanced excitation force of the shafting to reduce the unbalanced vibration response under the critical rotating speed, and the method can reduce the vibration amplitude of the critical rotating speed to a certain extent, but the required balance precision is very high to control the vibration amplitude of the shafting under the critical rotating speed to reach the qualified range; the second method is to suppress the vibration response at the critical speed by strengthening the fixed support strength of the upper part of the motor, and the hard support mode of jackscrews is generally adopted on site. However, the mode is not good for controlling the supporting strength of each point to be consistent, the central line of the shafting is easy to be inconsistent under the condition of poor control, the vibration reduction effect cannot be achieved, and the vibration is aggravated. Also, the rigid support may cause damage to the equipment when the vibrations are excessive.

Chinese patent publication No. CN203670596U discloses a simply supported beam type frequency adjustable dynamic vibration absorber, including base, step motor, slider, drive screw, metal beam, it has the dovetail to open on the base, and the lower tip of slider is the dovetail structure, and the upper end of slider is for having porose support arm, and the middle part of slider is for having the screwed through-hole, the slider have two, install in the dovetail under the tip of two sliders, the metal beam middle part has concentrated quality piece, the hole of two slider upper end support arms is passed respectively at the both ends of metal beam, the symmetry sets up reverse screw thread on the drive screw outer wall, drive screw passes the through-hole at two slider middle parts and cooperatees with the screw thread of two through-holes, step motor is connected to drive screw's first end. The need for outwardly extending space is reduced compared to cantilevered vibration absorbers. However, the vibration absorber disclosed by the patent is complex in structure and multiple in devices, so that the vibration absorber is easy to become a new vibration source, and the vibration reduction effect is not good.

Disclosure of Invention

The invention aims to solve the technical problem that the vibration absorber of the vertical rotating equipment in the prior art is poor in vibration attenuation effect.

The invention solves the technical problems through the following technical means: the utility model provides a magnetism guide rail bump leveller, includes support and two mutually perpendicular and fixed connection's magnetism guide rail, the support bottom is fixed on the motor, and the support upper end is connected with the connected node fixed connection of two magnetism guide rails, supports magnetism guide rail, the equal sliding connection of tip of every guide rail quality piece, every all be connected with a spring between the connected node of quality piece and two magnetism guide rails, the quality piece is for using magnetism guide rail as the winding coil of center pin, and a resistance R is passed through the wire at the both ends of coil and connects.

Under the action of the vibration absorber, the mass block consisting of the coil synchronously performs simple harmonic vibration on the magnetic guide rail, the coil cuts a magnetic induction line to generate induced electromotive force according to the electromagnetic induction principle, the coil is connected with the resistor R in series, the mass block absorbs vibration energy from the motor and converts the vibration energy into heat of the resistor R, and the energy generated by vibration is consumed in the resistor R, so that the vibration energy of the motor is reduced, and a better vibration reduction effect is realized.

Further, the spring is a spring damper.

Furthermore, the support includes four equal length supporting legs, and the one end of every supporting leg is all fixed on the motor, and the other end of every supporting leg links together and with the connected node fixed connection of two magnetism guide rails, the one end of four supporting legs encloses into the rectangle.

Further, the motor is a motor of a vertical rotating device.

The invention also provides a vibration reduction method of the magnetic guide rail vibration absorber, which comprises the following steps:

the method comprises the following steps: acquiring a vibration equation of a two-degree-of-freedom double-damping vibration system under the action of an excitation force of a motor;

step two: acquiring a complex equation of forced vibration in a stable state, solving the complex equation, and acquiring the force of a mass block acting on the upper surface of the motor according to the solution of the complex equation;

step three: selecting parameters of the vibration absorber to enable vibration to be absorbed;

step four: and adjusting the amplification factor to minimize the displacement of the motor under the action of the exciting force on a full frequency band, namely minimizing a complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state, and acquiring the damping ratio of the optimal vibration absorber and the natural frequency of the optimal vibration absorber.

Further, the first step comprises:

using formulasAcquiring a vibration equation of a two-degree-of-freedom double-damping vibration system under the action of an excitation force of a motor; 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, C₁Representing the damping coefficient of the motor, C₂Representing the damping coefficient, x, of the mass₁Representing the displacement of the motor, x₂Represents the displacement of the mass, and p (t) represents the excitation force.

Further, the second step comprises:

if the exciting force of the motor is simple harmonic force, the vibration equation of the two-freedom double-damping vibration system is transformed, and the complex equation of the forced vibration in a stable state is obtained as

Where ω denotes the excitation frequency, i denotes the complex imaginary unit, X₁A complex variable, X, representing the displacement of the motor₂A complex variable representing the displacement of the mass, P represents a complex variable of the excitation force,

solving a complex equation to obtain

By the formula

The force of the mass block acting on the upper surface of the motor is acquired,wherein, F₁Representing the force of the mass on the upper surface of the motor.

Further, the third step includes:

by the formula X₁₀＝P/(K-Mω²+iωC₁) Obtaining a complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state;

by the formula F₁₀＝(K+iωC₁)P/(K-Mω²+iωC₁) Obtaining the force of the motor itself, wherein F₁₀Representing the force of the motor itself;

by the formulaObtaining a relation between the vibration absorption performance and the frequency of the exciting force, wherein,

xi represents the vibration absorption coefficient, E₁Representing the vibration energy of the mass after acting on the motor, E₁₀Representing the vibration energy of the motor itself, V₁A complex variable, V, representing the speed of vibration of the mass after it has acted on the motor₁₀A complex variable representing the vibration speed of the motor itself;

by means of the strongest frequency equation of complex variable of vibration speed of motor

Selecting parameters of the vibration absorber to make xi>0, wherein ω_rThe strongest frequency of the complex variable of the vibration speed of the motor itself.

Further, the fourth step includes:

order toWherein β represents an amplification factor and

wherein, ω is_nTo representThe natural frequency of the motor, mu, represents the ratio of the mass to the mass of the motor, omega₀Showing the natural frequency, ζ, of the vibration absorber₁Represents the damping ratio of the motor and

ζ₂represents the damping ratio of the vibration absorber and

the amplification factor is adjusted to ensure that the displacement of the motor under the action of the exciting force is minimum in a full frequency band, namely the complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state is minimum.

Further, the process of adjusting the amplification factor is:

step 401: taking a frequency band gamma in the neighborhood of the natural frequency of the motor_a≤ω₁≤γ_bWherein γ is_a＝0.7ω_n，γ_b＝1.3ω_n；

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 a calculation formula of the amplification factor to calculate the value of the amplification factor in the frequency band;

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 the step 402 until the minimum value of the amplification factor is obtained, taking the damping ratio of the vibration absorber at the moment as the damping ratio of the optimal vibration absorber, and taking the natural frequency of the vibration absorber at the moment as the natural frequency of the optimal vibration absorber.

The invention has the advantages that:

(1) under the action of the vibration absorber, the mass block consisting of the coil synchronously performs simple harmonic vibration on the magnetic guide rail, the coil cuts a magnetic induction line to generate induced electromotive force according to the electromagnetic induction principle, the coil is connected with the resistor R in series, the mass block absorbs vibration energy from the motor and converts the vibration energy into heat of the resistor R, and the energy generated by vibration is consumed in the resistor R, so that the vibration energy of the motor is reduced, and a better vibration reduction effect is realized.

(2) The method selects the parameters of the vibration absorber to absorb the vibration, adjusts the amplification factor to minimize the displacement of the motor under the action of the exciting force in a full frequency band, obtains the optimal damping ratio of the vibration absorber and the optimal natural frequency of the vibration absorber, analyzes and calculates the vibration attenuation effect, and optimizes the vibration attenuation effect.

Drawings

Fig. 1 is a front view of a magnetic guide rail vibration absorber according to an embodiment of the present invention;

fig. 2 is a top view of a magnetic rail vibration absorber according to an embodiment of the present invention;

fig. 3 is a schematic diagram illustrating connection between a coil and a resistor R in a mass block in a magnetic rail vibration absorber according to an embodiment of the present invention;

FIG. 4 is a physical model of a single-degree-of-freedom single-damping vibration system in a magnetic guide rail vibration absorber according to an embodiment of the present invention;

FIG. 5 is a physical model of a two-degree-of-freedom double-damping vibration system in a magnetic guide rail vibration absorber according to an embodiment of the present invention;

fig. 6 is a flowchart of a vibration reduction method of a magnetic rail vibration absorber according to an embodiment of the present invention.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the embodiments of the present invention, and it is obvious that the described embodiments are some embodiments of the present invention, but not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

As shown in fig. 1 to 3, a magnetic rail vibration absorber includes a bracket 4 and two magnetic rails 2 perpendicular to each other and fixedly connected.

The support 4 comprises four equal-length supporting legs, one end of each supporting leg is fixed on the motor 5, and the motor 5 is the motor 5 of the vertical rotating equipment. The other end of each supporting leg is connected together and fixedly connected with the connecting node of the two magnetic guide rails 2, and one end of each of the four supporting legs is enclosed into a rectangle.

The upper end of the support 4 is fixedly connected with the connecting node of the two magnetic guide rails 2 to support the magnetic guide rails 2, the two magnetic guide rails 2 are perpendicular to each other and respectively correspond to the working medium flowing direction and the perpendicular working medium flowing direction of the vertical motor 5, the frequency parameters of the two groups of fin-shaped vibration absorbers can be independently adjusted and respectively correspond to different vibration frequencies in the two directions, and the vibration reduction effect is improved.

The end part of each magnetic guide rail 2 is connected with a mass block 1 in a sliding mode, the weight of the mass block 1 can be adjusted through replacement, and the frequency width of damping is improved.

And a spring 3 is connected between the connection node of each mass block 1 and each magnetic guide rail 2, and 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 around the magnetic guide rail as a central axis, and two ends of the coil are connected with a resistor R (not shown) through a conducting wire.

Continuing to refer to fig. 1 to 3, the vibration absorbers are arranged according to the working medium flowing direction (X direction) and the vertical working medium flowing direction (Y direction) of the motor 5, when the motor 5 vibrates greatly, the vibration in the X direction causes the vibration absorber group consisting of the mass block C, the mass block D and the spring damper to vibrate, and the proper elastic coefficients of the mass block C, D and the spring damper are designed according to the relevant parameters of the main system with the motor 5 as the main body, so that the auxiliary vibration absorber system can absorb part of the vibration energy in the X direction of the main system, and the effect of reducing the vibration amplitude in the X direction is achieved.

Similarly, the vibration absorber set composed of the mass block A, B and the spring damper can absorb vibration energy in the Y direction, and the vibration amplitude effect in the Y direction is reduced.

In the plane formed by mutually perpendicular X, Y directions, the vibration in each direction can be decomposed into the synthesis of X, Y two-direction vibration, so under the action of X, Y-direction two groups of vibration absorbers, the aim of reducing the vibration amplitude in each direction of the horizontal plane can be achieved.

Under the effect of bump leveller, the quality piece 1 that comprises the coil carries out simple harmonic vibration in step on magnetic guide 2 under the effect of bump leveller, according to the electromagnetic induction principle, coil cutting magnetic induction line produces induced electromotive force, and coil series resistance R absorbs vibration energy with quality piece 1 from motor 5 and turns into resistance R's calorific capacity, consumes the energy that the vibration produced in resistance R to reduce the vibration energy of motor, realize better damping effect.

Neglecting the influence of some secondary factors, the motor 5 can be simplified into a physical model containing a single-degree-of-freedom single-damping vibration system shown in fig. 4, and if a vibration absorber consisting of k-m-C2 is added, the vibration absorber becomes a two-degree-of-freedom double-damping vibration system shown in fig. 5, as shown in fig. 6, and the invention also provides a vibration reduction method of the magnetic guide rail vibration absorber, wherein the method comprises the following steps:

step S1: acquiring a vibration equation of a two-degree-of-freedom double-damping vibration system under the action of an excitation force of a motor 5; the specific process is as follows:

using formulas

Acquiring a vibration equation (excluding gravity and generated initial displacement) of the two-degree-of-freedom double-damping vibration system under the action of the exciting force of the motor 5; wherein M represents the mass of the motor 5, M represents the mass of the mass 1, K represents the elastic coefficient of the motor 5, K represents the elastic coefficient of the mass 1, C₁Representing the damping coefficient, C, of the motor 5₂Representing the damping coefficient, x, of the mass 1₁Representing the displacement, x, of the motor 5₂The displacement of the mass 1 is shown, and p (t) the excitation force.

Step S2: acquiring a complex equation of forced vibration in a stable state, solving the complex equation, and acquiring 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:

the excitation force p (t) of the mechanical vibration is generally a periodic external force. If the exciting force of the motor 5 is simple harmonic force, the vibration equation of the two-freedom-degree double-damping vibration system is transformed, and the complex equation of the forced vibration in a stable state is obtained as

Where ω denotes the excitation frequency, i denotes the complex imaginary unit, X₁A complex variable, X, representing the displacement of the motor 5₂The complex variable representing the displacement of the mass block 1, P the complex variable of the excitation force, and solving a complex equation to obtain

By the formulaAcquiring the force of the mass block 1 acting on the upper surface of the motor 5, wherein F₁Representing the force of the mass 1 on the upper surface of the motor 5.

Step S3: selecting parameters of the vibration absorber to enable vibration to be absorbed; the specific process is as follows:

by the formula X₁₀＝P/(K-Mω²+iωC₁) Obtaining a complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state;

by the formula F₁₀＝(K+iωC₁)P/(K-Mω²+iωC₁) Obtaining the force of the motor 5 itself, wherein F₁₀Representing the force of the motor 5 itself; this corresponds to the case where m is 0 and C2 is 0 in the system of fig. 5.

Under the same excitation force, whether a shock absorber consisting of k-m-C2 is added or not, the vibration energy E1 of the motor 5 and the force F1 of the mass block 1 acting on the upper surface of the motor 5 are usually different, and the change condition has a direct relation with the frequency of the excitation force. Next, a detailed analysis is made as to the relationship between the vibration-absorbing performance of the vibration absorber and the frequency of the exciting force (i.e., the frequency characteristic of vibration absorption).

By the formulaObtaining a relation between the vibration absorption performance and the frequency of the exciting force, wherein,xi represents the vibration absorption coefficient, E₁Representing the vibration energy, E, of the mass 1 after it has acted on the motor 5₁₀Representing the vibration energy, V, of the motor 5 itself₁A complex variable, V, representing the speed of vibration of the mass 1 after it has acted on the motor 5₁₀A complex variable representing the vibration speed of the motor 5 itself;

apparent xi>1, when xi>At 0, F₁₀/F₁(or E)₁₀/E₁)>1, showing that after the vibration absorber is added, the vibration of the K-M-C1 damping vibration system is absorbed; when-1<ξ<At 0, F₁₀/F₁(or E)₁₀/E₁)<1, after a damping vibration absorber is added during the watch, the vibration of a K-M-C1 damping vibration system is strengthened; when xi is 0, F₁₀/F₁(or E)₁₀/E₁) 1, the damped absorber is shown to have no effect on the K-M-C1 vibration system.

The principle of designing the absorber is therefore to choose the appropriate k, m, C2 parameters such that ξ > 0.

When the mechanical system is in operation, the vibration (e.g. vibration speed V) can be measured₁₀) The frequency spectrum of (C) can be obtained by mechanically adding a vibration system of vibration absorbers k to m to C2, and selecting the parameters k, m and C2 to control the interval (ω)_min，ω_max) As much as possible of V₁₀The strong frequency of the medium vibration enables part of the vibration energy of the mechanical damping vibration system K-M-C1 to be absorbed by the vibration absorbers and consumed in the damping C2, so that the mechanical vibration is weakened.

At V₁₀Selecting the component with strong vibration, and setting the frequency as omega_rSelecting parameters k, m and C2 of the vibration absorber to make omega_rAt its natural frequency of dampingAnd natural frequencyNamely:

then:

when the mechanical system is at frequency omega_rThe vibration component of (c) is considerably attenuated while at ω_rThe vibrations in the frequency domain, which are rather large on both sides, can be damped to different degrees, so that the total vibration is attenuated.

When the parameters of the vibration absorber are selected, the vibration absorbing frequency range (omega) is obtained when the values of k, m and C2 are larger_min，ω_max) The larger the vibration absorption, 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 is less than or equal to M, K is less than or equal to K, and the sizes of K, M and C2 are properly adjusted to ensure the optimal vibration absorption state.

Step S4: the amplification factor is adjusted to ensure that the displacement of the motor 5 under the action of the exciting force is minimum in a full frequency band, namely the complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state is minimum, 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:

order to

Wherein β represents an amplification factor and

wherein, ω is_nDenotes the natural frequency of the motor 5, mu denotes the ratio of the mass 1 to the mass of the motor 5, omega₀Showing the natural frequency, ζ, of the vibration absorber₁Represents the damping ratio of the motor 5 and

ζ₂represents the damping ratio of the vibration absorber and

the amplification factor is adjusted to ensure that the displacement of the motor 5 under the action of the exciting force is minimum in a full frequency band, namely the complex solution of the vibration of the single-degree-of-freedom vibration system in a stable state is minimum.

Wherein, the process of adjusting the amplification factor is as follows:

step 401: taking a frequency band gamma in the vicinity of the natural frequency of the motor 5_a≤ω₁≤γ_bWherein γ is_a＝0.7ω_n，γ_b＝1.3ω_n；

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 a calculation formula of the amplification factor to calculate the value of the amplification factor in the frequency band;

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 the step 402 until the minimum value of the amplification factor is obtained, taking the damping ratio of the vibration absorber at the moment as the damping ratio of the optimal vibration absorber, and taking the natural frequency of the vibration absorber at the moment as the natural frequency of the optimal vibration absorber.

The above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.