CN201261011Y - Anti-resonance vibrating screen - Google Patents

Abstract

The utility model relates to an antiresonance vibration sieve which belongs to the technical field of vibration machines and comprises a sieve box, a shock excitation body, a main vibration spring, an exciter, an isolation spring, a base, a motor, and the like, wherein the sieve box is an upper body which is a working part of the antiresonance vibration sieve, the shock excitation body is a lower body which is a driving part of the antiresonance vibration sieve, the exciter is arranged on the shock excitation body, the sieve box is connected with the shock excitation body through the main vibration spring, the shock excitation body is arranged on the base through the isolation spring, and the motor is arranged on a motor bracket and is connected with the exciter through a transmission shaft. The utility model has the advantages that the sieve box of the antiresonance vibration sieve is provided with the exciter, the total mass of vibration can be reduced by 20-30 percent, the exciting force is reduced, and the motor power is reduced, thereby the energy is saved. The main vibration spring is arranged along the sieve box lateral plate, the stress of the sieve box is even so as to be favorable to prolonging the service life of the sieve; the exciter is arranged on the lower body which is nearly not vibrated, the rigidity and the strength are easily ensured. The noise of the integral sieve is obviously lowered.

Description

A kind of anti-resonance vibrating sifter

Technical field

The utility model relates to a kind of vibrating machine technical field, be suitable for classification, the sintering deposit of coal classification, mineral classification, and the classification of other various diffusing shape things use.

Background technology

Vibrating machine is to utilize vibration to finish a big class plant equipment of various technical process, as jigging conveyer, vibratory sieve, vibration drying machine, vibrated roller etc., the kind of tradition vibratory sieve is a lot, and dividing by purposes has coal grading vibratory sieve, ore classification vibratory sieve, cold jig, hot jig etc.; By the division of screening principle probability screen, uniform thickness sieve, probability uniform thickness sieve etc. are arranged; Divide modes such as flexible link-type, electromagnetic type, inertia-type, pneumatic and hydraulic pressure by drive principle; Also can divide by dynamics, as by whether utilizing resonance principle to divide, off-resonance sieve and resonance screens be arranged, be linearity or non-linear division by vibrational system, and linear vibratory sieve and Non-Linear Vibration sieve is arranged;

At present, large-scale vibrating screen is operated in super resonance state far away more, is large-scale off-resonance inertia-type vibratory sieve, and large-scale off-resonance inertia-type vibratory sieve comprises following a few part: screen box (going up plastid), two-stage vibration isolation frame (following plastid), an isolation spring, vibrator, two-stage vibration isolation spring, buffer, motor, power transmission shaft, electric machine support, the shortcoming of this kind vibratory sieve is: no matter resonance of traditional vibratory sieve or off-resonance, vibrator all is mounted on the plastid, needs reinforcement around the vibrator, and mass of vibration is bigger, screen box is subjected to the direct effect of exciting force, therefore the screen box fatiguability destroys, and noise is bigger, and vibration isolating effect is relatively poor, must be seated in screen box on the two-stage vibration isolation frame in order to improve vibration isolating effect for the off-resonance sieve, complete machine weight is bigger, and the screen box fault rate is higher, and the life-span is also undesirable.

The utility model content

For solving the deficiency of above structure, the purpose of this utility model proposes a kind of anti-resonance vibrating sifter, utilize its vibrator to be installed in down on the plastid, thereby the structure of work body is simplified greatly, mass of vibration can reduce 20-30%, exciting force also can reduce thereupon, because the work body is not subjected to the direct effect of exciting force, life-span can improve, following plastid vibrates hardly, guarantee the requirement of rigidity and intensity during design easily, vibrator can design by dead load basically, and the noise of complete machine can obviously reduce.

The utility model structural design is achieved in that anti-resonance vibrating sifter includes: screen box is plastid under last plastid, excitor are, main vibration spring, vibrator, isolation spring, basis, motor, power transmission shaft, electric machine support; Its connection: plastid is the working portion of anti-resonance vibrating sifter on the screen box, plastid is a drive part under the excitor, vibrator is installed on excitor, link to each other by main vibration spring between screen box and the excitor, excitor is seated on the basis by isolation spring, motor is installed on the motor frame, and links to each other with vibrator by power transmission shaft; Main vibration spring can be the combination of the helical spring combination of flat spring, flat spring and tension and compression, flat spring and reversal connection formula compression rubber spring or the combination of flat spring and shear-type rubber spring.

The characteristics of anti-resonance vibrating sifter:

The tradition vibratory sieve is operated in super resonance state far away or is operated in low critical Near resonance oscillating state, and anti-resonance vibrating sifter then is operated in the antiresonance state, and under the antiresonance state, following plastid is almost motionless, obtains vibration isolating effect preferably easily;

The tradition vibratory sieve, vibrator is installed on the plastid screen box, and anti-resonance vibrating sifter then is installed in down on the plastid excitor, there is not vibrator on the screen box, reduced mass of vibration, the height of screen box can reduce, and has saved vibrator and reinforced required quality, thereby mass of vibration can further reduce, mass of vibration can reduce 20-30% altogether, because mass of vibration has reduced, exciting force can reduce thereupon, power of motor has also just reduced, and helps energy-conservation;

Excitor is to pass through main vibration spring to the connection of screen box, main vibration spring rigidity is bigger, plastid is stressed evenly up and down in order to make, main vibration spring should be along the layout that distributes of moving towards of sieve box side plate, and main vibration spring can be: the combination of the helical spring combination of flat spring, flat spring and tension and compression, flat spring and reversal connection compression-type rubber spring or the combination of flat spring and shear-type rubber spring;

If main vibration spring option board spring, the length direction of flat spring should be vertical with direction of vibration; As main vibration spring option board spring and the helical spring combination of tension and compression, the length direction of flat spring should be vertical with direction of vibration, and the helical spring length direction of tension and compression should be parallel with direction of vibration.

If the combination of main vibration spring option board spring and reversal connection formula compression rubber spring, the length direction of flat spring should be vertical with direction of vibration, and the length direction of reversal connection formula compression rubber spring should be parallel with direction of vibration; As the combination of main vibration spring option board spring and shear-type rubber spring, the length direction of flat spring should be vertical with direction of vibration, and the shear direction of shear-type rubber spring should be parallel with direction of vibration.

Vibrator can adopt motor synchronizing or two kinds of structures of forced synchronism, with motor synchronizing or the operation of forced synchronism dual mode, as adopting the motor synchronizing structure, no any mechanically contact between two vibrators, the self synchronization theory synchronous operation during by antiresonance; As adopt forced synchronism structure, forced synchronism can take the various kinds of drive such as gear drive, cog belt transmission, V-belt transmission.

Vibrator is installed in down on the plastid, strengthening quality around vibrator quality and the vibrator can be as the part of following plastid quality, in fact reduced the quality of time plastid, because following plastid is not a working portion, its shape and size are not subjected to the restriction of technological requirement, descend plastid to vibrate hardly in addition, and rigidity and requirement of strength guarantee easily, screen box and the excitor certain angle that can tilt, but also level is installed;

The kinetic parameter of anti-resonance vibrating sifter, its kinetic parameter mainly contains:

Plastid mass ratio up and down $\mathrm{\&mu;}=\frac{m_2}{{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">m</figure-callout>}}_1},$ M in the formula ₁The quality of plastid under being, m ₂Be the quality that goes up plastid, the range of choice of mass ratio μ is 0.5-6, and mass ratio μ selects than fractional value, will cause under the excitor plastid weight bigger than normal, and complete machine weight is bigger;

The antiresonant frequency ratio $a=\frac{{\mathrm{\&omega;}}_a}{{\mathrm{\&omega;}}_0},$ In the formula ${\mathrm{\&omega;}}_a=\sqrt{{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">k</figure-callout>}}_2/{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">m</figure-callout>}}_2}$ Be antiresonant frequency; ${\mathrm{\&omega;}}_0=\sqrt{{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">k</figure-callout>}}_1/{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">m</figure-callout>}}_1},$ Be the intrinsic frequency of following plastid subsystem, antiresonant frequency is 1-15 than the span of a, gets higher value when operating frequency is high, gets smaller value when operating frequency is low, and two resonance points helped the stable of amplitude from must be far away when antiresonant frequency was got higher value than a;

Main vibration spring rigidity k ₂, main vibration spring rigidity k ₂=m ₂ω _a ², m in the formula ₂Be the mass of vibration of plastid on the screen box, ω _aBe antiresonant frequency.

The anti-resonance vibrating sifter operation principle is as shown in Figure 1: the equation of motion that can directly list system according to mechanical model:

$\left[\begin{array}{cc}{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">m</figure-callout>}}_1& 0\\ 0& m_2\end{array}\right]\left\{\begin{array}{c}{\stackrel{\&CenterDot;\&CenterDot;}{x}}_1\\ {\stackrel{\&CenterDot;\&CenterDot;}{x}}_2\end{array}\right\}+\left[\begin{array}{cc}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">k</figure-callout>}}_1+k_2& {-k}_2\\ {-k}_2& k_2\end{array}\right]\left\{\begin{array}{c}{x}_1\\ x_2\end{array}\right\}=\left\{\begin{array}{c}F\sin \mathrm{\&omega;t}\\ 0\end{array}\right\}---\left(1\right)$

F is an amplitude of exciting force in the formula, establish X}={B}sin ω t, X} is the displacement column vector, and substitution (1) formula then gets matrix equation:

{F}＝[Z]{B} (2)

In the formula, F} is the nodal force vector magnitude, $\left\{F\right\}=\left\{\begin{array}{c}{\mathrm{<figure-callout\; id="1"\; label="F"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">F</figure-callout>}}_1\\ 0\end{array}\right\};$ B} is a displacement column vector amplitude, $\left\{B\right\}=\left\{\begin{array}{c}{B}_1\\ {\mathrm{<figure-callout\; id="2"\; label="B"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">B</figure-callout>}}_2\end{array}\right\};$ [Z] is the displacement impedance matrix, $\left[Z\right]=\left[\begin{array}{cc}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">k</figure-callout>}}_1+k_2-{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">m</figure-callout>}}_1{\mathrm{\&omega;}}^2& {-k}_2\\ {-k}_2& k_2-{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">m</figure-callout>}}_2{\mathrm{\&omega;}}^2\end{array}\right].$

Can get by formula (1):

{B}＝[Z] ^-1{F}＝[H]{F}

In the formula, [H] is admittance matrix, $\left[H\right]={\left[Z\right]}^{-1}=\frac{1}{\mathrm{\&Delta;}}\left[\begin{array}{cc}{k}_2-{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">m</figure-callout>}}_2{\mathrm{\&omega;}}^2& k_2\\ k_2& {\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">k</figure-callout>}}_1+k_2-{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">m</figure-callout>}}_1{\mathrm{\&omega;}}^2\end{array}\right],$ And $\mathrm{\&Delta;}=\left|\begin{array}{cc}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">k</figure-callout>}}_1+k_2-{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">m</figure-callout>}}_2{\mathrm{\&omega;}}^2& {-k}_2\\ {-k}_2& k_2-{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">m</figure-callout>}}_2{\mathrm{\&omega;}}^2\end{array}\right|.$ Therefore have

$\left\{\begin{array}{c}{B}_1\\ {\mathrm{<figure-callout\; id="2"\; label="B"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">B</figure-callout>}}_2\end{array}\right\}=\frac{1}{\mathrm{\&Delta;}}\left[\begin{array}{cc}{k}_2-{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">m</figure-callout>}}_2{\mathrm{\&omega;}}^2& k_2\\ k_2& {\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">k</figure-callout>}}_1+k_2-{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">m</figure-callout>}}_1{\mathrm{\&omega;}}^2\end{array}\right]\left\{\begin{array}{c}{\mathrm{<figure-callout\; id="1"\; label="F"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">F</figure-callout>}}_1\\ 0\end{array}\right\}=\frac{{\mathrm{<figure-callout\; id="1"\; label="F"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">F</figure-callout>}}_1}{\mathrm{\&Delta;}}\left[\begin{array}{c}{k}_2-{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">m</figure-callout>}}_2{\mathrm{\&omega;}}^2\\ k_2\end{array}\right]---\left(3\right)$

By formula (3) as can be known, when $\mathrm{\&omega;}=\sqrt{\frac{k_2}{{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">m</figure-callout>}}_2}}$ The time, initial point antiresonance, at this moment B appear in system ₁=0, and

${\mathrm{<figure-callout\; id="2"\; label="B"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">B</figure-callout>}}_2=-\frac{F_1}{{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">k</figure-callout>}}_2}$

Because all there is certain damping in real system, plastid m ₁Amplitude can not be zero, its size depends on the size of damping.At this moment the dynamic loading of passing to the basis is:

P＝B ₁k ₁

Because the damping of real system is generally less, so it is also littler than general two-stage vibration isolation system to pass to the dynamic loading on basis, the antiresonance bobbing machine is with plastid m ₂Be the work body, vibrator then is installed in plastid m ₁On, the structure of work body is simplified greatly, mass of vibration can reduce 20%～30%, and exciting force also can reduce thereupon, because plastid m ₂Be not subjected to the direct effect of exciting force, the life-span of body can improve, and vibrator is installed in plastid m ₁On, have very big flexibility during design, guarantee the requirement of rigidity and intensity easily, the noise of complete machine can reduce greatly, but the antiresonance bobbing machine requires excited frequency more stable, and amplitude is subject to the influence that inventory changes in addition.

The amplitude control of anti-resonance vibrating sifter

In the ordinary course of things, the bond quality of material is very little, less than 20% of screen box quality, and the undulate quantity of material is littler, less than 20% of inventory, by the choose reasonable kinetic parameter, can make near the amplitude-frequency response of antiresonance point milder, make the fluctuation of material can not cause harmful effect to the operation of screen(ing) machine;

Run into special circumstances, inventory changes greatly or the unusual instability of excited frequency, cause the screen(ing) machine cisco unity malfunction, working amplitude can not be satisfied the demand or vibration isolating effect when bad, the method that solves is that frequency converter is connected with drive motors, can adjust excited frequency with frequency converter, change the operating point, make screen(ing) machine recover operate as normal;

The excited frequency of adjusting frequency converter has two kinds of methods: manually adjust, manually adjustment only is suitable for inventory or the not frequent situation of excited frequency variation; By the computer adjustment, the computer adjustment is suitable for inventory or excited frequency changes frequent situation, and can realize optimum control.

When manually adjusting, the connection block diagram of control system as shown in Figure 8, when computer was regulated automatically, the connection block diagram of control system was as shown in Figure 9.

Make the same plastid amplitude minimum at present of plastid amplitude stability on the anti-resonance vibrating sifter, can take following three kinds of control strategies:

Only plastid is gone up in monitoring:

When anti-resonance vibrating sifter produces fluctuation in inventory, can make the plastid amplitude stability in design load, the amplitude of following plastid also just is in minimum state approx, be easy to realize the stable control of plastid amplitude with PID control, but this control method, last plastid amplitude can be more accurate be stabilized in design load, but following plastid amplitude is not owing to controlled, can only realize the minimum of a value that is similar to, when the material bond quality is no more than 30% of plastid quality, the material undulate quantity is not more than under 30% the situation of inventory, and this control method can satisfy requirement of engineering.

Only monitor plastid down:

When anti-resonance vibrating sifter produces fluctuation in inventory, as long as control plastid amplitude down is in minimum state all the time, the amplitude of last plastid is also just approx near design load, but adopt this control method, following plastid amplitude can remain on minimum state, but last plastid amplitude is not owing to controlled, can only equal design load approx, but when the material bond quality is no more than 30% of plastid quality, the material undulate quantity is not more than under 30% the situation of inventory, and this control method can satisfy requirement of engineering.

The optimum control that plastid is up and down monitored simultaneously:

Make on the anti-resonance vibrating sifter plastid amplitude stability in design load,, can make the target function value minimum by controlling excited frequency, promptly the amplitude sum of the undulate quantity of last plastid amplitude and following plastid as object function with plastid amplitude minimum at present

min(k ₁ΔB ₂+k ₂B ₁)(ΔB ₂≥0，k ₁≤1，k ₂≤1)

B in the formula ₁Be following plastid amplitude; Δ B ₂Undulate quantity for last plastid amplitude; k ₁, k ₂Be weight coefficient.

Description of drawings

Fig. 1 is anti-resonance vibrating sifter mechanical model figure of the present invention;

Fig. 2 is the anti-resonance vibrating sifter structure principle chart;

Fig. 3 is the figure of anti-resonance vibrating sifter lateral projection;

Fig. 4 is the anti-resonance vibrating sifter horizontal mounting structure figure of plastid up and down;

Structure chart when Fig. 5 is flat spring and helical spring combination for the anti-resonance vibrating sifter main vibration spring;

Fig. 6 is that the anti-resonance vibrating sifter vibrator is at following plastid external structure figure;

Fig. 7 is a up and down plastid mass ratio hour structure chart of anti-resonance vibrating sifter;

Fig. 8 manually adjusts the connection block diagram for anti-resonance vibrating sifter;

Fig. 9 adjusts the connection block diagram automatically for anti-resonance vibrating sifter.

The specific embodiment

The utility model detailed structure is illustrated with accompanying drawing with the following Examples.

Fig. 1 is anti-resonance vibrating sifter mechanical model figure of the present invention, does not consider damping, m among the figure ₂Be the quality that goes up plastid, the working portion of this machine, following plastid m ₁On the inertia-type vibrator is housed, its exciting force is a simple harmonic quantity power, k ₂Be main vibration spring rigidity, k ₁Be isolation spring rigidity, x ₁Be plastid displacement down, x ₂Be last plastid displacement, concrete vibratory sieve parameter is drawn by equation;

The utility model structure as shown in Figure 2, it is the working portion of anti-resonance vibrating sifter that screen box (1) is gone up plastid, excitor (2) plastid down is a drive part, vibrator (4) is installed on excitor (2), link to each other by main vibration spring (3) between screen box (1) and the excitor (2), excitor (2) is seated on the basis (6) by isolation spring (5), and motor (7) is installed on the electric machine support (9), and links to each other with vibrator (4) by power transmission shaft (8); The present embodiment main vibration spring is a flat spring, divides many groups, every group of multi-disc, and the main vibration spring global stiffness is convenient to regulate, up and down plastid mass ratio μ=m ₂/ m ₁Bigger, m ₁Plastid quality under being, m ₂Be the quality that goes up plastid, complete machine weight is lighter; Fig. 4 plastid level up and down installs, and all the other are identical with figure 2, and Fig. 5 main vibration spring is the combination of flat spring and helical spring (10), and flat spring can not divide into groups, and also can divide many groups, every group of multi-disc, and helical spring (10) is a drawing-pressing spring, all the other are identical with Fig. 2; Fig. 6 vibrator is not to be contained in down in the plastid, and is mounted in down the outside of plastid, and promptly so-called box vibrator is convenient to the modularization of vibrator, and all the other are identical with Fig. 2; Fig. 7 is the plastid mass ratio up and down $\mathrm{\&mu;}=\frac{m_2}{{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">m</figure-callout>}}_1}$ Less, m ₁The quality of plastid under being, m ₂Be the quality that goes up plastid, complete machine weight is heavier, but obtains bigger antiresonant frequency ratio easily $a=\frac{{\mathrm{\&omega;}}_a}{{\mathrm{\&omega;}}_0},$ In the formula ${\mathrm{\&omega;}}_a=\sqrt{{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">k</figure-callout>}}_2/{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="Y200820014475E00101.png,Y200820014475E00121.png"\; state="\{\{state\}\}">m</figure-callout>}}_2},$ Be antiresonant frequency; k ₂Be the rigidity of main vibration spring, ${\mathrm{\&omega;}}_0=\sqrt{{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">k</figure-callout>}}_1/{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="Y200820014475E00131.png"\; state="\{\{state\}\}">m</figure-callout>}}_1}$ Be the intrinsic frequency of following plastid subsystem, k ₁Rigidity for isolation spring; Fig. 8 manually adjusts to connect block diagram, and manually adjustment only is suitable for inventory or excited frequency and changes when frequent; When Fig. 9 was adjustment automatically, by the computer adjustment, the computer adjustment is suitable for inventory or excited frequency changes frequent situation, and can realize optimum control.

Claims (7)

1, a kind of anti-resonance vibrating sifter, its structure includes: going up plastid is screen box, plastid is excitor, main vibration spring, isolation spring, vibrator down, it is characterized in that screen box (1) is connected with excitor (2) by main vibration spring (3), excitor (2) is seated on the basis (6) by isolation spring (5), vibrator (4) is housed on excitor (2), and motor (7) links to each other with vibrator (4).

2, by the described anti-resonance vibrating sifter of claim 1, it is characterized in that excitor (2) is by main vibration spring (3) to the connection of screen box (1), main vibration spring (3) is along the setting of moving towards of screen box (1) side plate, and main vibration spring (3) can be: the combination of the helical spring combination of flat spring, flat spring and tension and compression, flat spring and reversal connection formula compression rubber spring or the combination of flat spring and shear-type rubber spring.

3, by the described anti-resonance vibrating sifter of claim 2, it is characterized in that main vibration spring option board spring, the length direction of flat spring should be vertical with direction of vibration, if main vibration spring option board spring and the helical spring combination of tension and compression, the length direction of flat spring should be vertical with direction of vibration, and the helical spring length direction of tension and compression should be parallel with direction of vibration.

4, by the described anti-resonance vibrating sifter of claim 2, it is characterized in that the combination of main vibration spring option board spring and reversal connection formula compression rubber spring, the length direction of flat spring should be vertical with direction of vibration, reversal connection formula compression rubber spring length direction should be parallel with direction of vibration, if the combination of main vibration spring option board spring and shear-type rubber spring, the flat spring length direction should be vertical with direction of vibration, and the shear direction of shear-type rubber spring should be parallel with direction of vibration.

5, by the described anti-resonance vibrating sifter of claim 1, it is characterized in that vibrator can adopt motor synchronizing or two kinds of structures of forced synchronism, the operation of motor synchronizing or forced synchronism dual mode is arranged, if adopt the motor synchronizing structure, no any mechanically contact between two vibrators, self synchronization theory synchronous operation during by antiresonance, if adopt the forced synchronism structure, forced synchronism can be taked gear drive, cog belt transmission or V-belt transmission.

6 by the described anti-resonance vibrating sifter of claim 1, it is characterized in that: its quality of plastid is 0.5-6 than range of choice under the described upward plastid.

7,, it is characterized in that this anti-resonance vibrating sifter motor (7) and vibrator (4) become one, and promptly constitute vibrating motor by the described anti-resonance vibrating sifter of claim 1.

8, by the described anti-resonance vibrating sifter of claim 1, it is characterized in that described motor (7) can link to each other with vibrator (4) by power transmission shaft.

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