CN203257960U - Modular-parameter-adjustable dynamic shock absorber - Google Patents

Abstract

The utility model discloses a modular-parameter-adjustable dynamic shock absorber. The modular-parameter-adjustable dynamic shock absorber is mainly composed of a base, a connecting seat, a hinged support, a lower lever arm, an upper lever arm, a fine tuning spring, a guiding rail, a mass block, a tray, a primary spring, a fine tuning damper, a primary damper and parallel holes. The base and the connecting seat are connected through bolts, and the hinged support is connected to the connecting seat through bolts. The spring and the dampers are of modularized structures, the lower lever arm and the upper lever arm are connected through a connecting shaft, and the tray passes through a connecting block and is hinged to the upper lever arm through the connecting shaft. The mass block is fixed on the tray through locking bolts, a slide is arranged in the tray, the slide and the guiding rail can form a sliding pair, and the tray is connected with the primary damper and primary spring. The connecting seat is connected with the primary damper and the primary spring, and a parallel pin is arranged on the tray. The modular-parameter-adjustable dynamic shock absorber aims to overcome the defects that an existing dynamic shock absorber is poor in transportability and unchangeable in parameter.

Description

The adjustable dynamic shock absorber of modularization parameter

Technical field:

The utility model relates to a kind of parameter adjustable type dynamic shock-absorbing device, applicable to different damper types, different vibration damping demand of installing in surface, the different parameters situation, belongs to mechanical vibration mechanics field.

Background technique:

At present, dynamic shock absorber has been mainly two types of damping dynamic shock absorber and non-damped dynamic vibration absorbers.Non-damped dynamic vibration absorber is mainly used in the vibration damping occasion that frequency content is fixed, fluctuates less; And have the damping dynamic shock absorber to be mainly used in the interior vibration damping occasion of a certain frequency band.But no matter which kind of vibration damper all designs for individual device, is applied in stationary applica-tions, and self parameter change is difficulty, in case design is finished, himself parameter is just determined, and is immutable, portable poor.Even be applied to the same class object, during to Different Individual, owing to vibration frequency difference, installation surface differences etc. factor, all need redesign, make, equip vibration damping equipment, bring very large inconvenience to people.

Summary of the invention:

Goal of the invention: the utility model proposes a kind of modular power vibration damper, its purpose is to overcome the shortcoming and defect that the aspects such as existing dynamic shock absorber portability is poor, parameter is immutable exist.

The utility model is achieved through the following technical solutions:

The adjustable dynamic shock absorber of a kind of modularization parameter, it is characterized in that: mainly by base, connection seat, hinged-support, lever underarm, lever upper arm, fine setting spring, guide rail, mass block, pallet, main spring, fine setting damping, main damping, hole in parallel form this dynamic shock absorber; Base is connected with bolt with connection seat, to realize the installation requirements of different surfaces situation; Hinged-support is connected on the connection seat with bolt; Spring and damping have modular construction, and the lever underarm links to each other by coupling shaft with the lever upper arm, are fixed on the hinged-support, to realize the fine setting of damping and spring parameter; Pallet is hinged on the lever upper arm through contiguous block by coupling shaft; The fixing hole of size is arranged in the mass block, cooperatively interact with pallet, be fixed on the pallet by lock bolt, mass parameter is regulated; Pallet is provided with slideway, can form sliding pair with guide rail, and pallet is slided along fixed-direction; Also be provided with main damping and main spring coupling arrangement on the pallet, connect with main damping and main spring; Connection seat is provided with coupling arrangement equally, connects with main damping and main spring; Pallet has and sells through joint efforts, and realizes being connected in parallel of dynamic shock absorber.

Base and connection seat and hinged-support are provided with the fixing connecting hole of size and position, by bolton, to install at different surfaces.

Spring and damping have modular construction, can select dissimilar being connected on the hinged-support; Lever underarm, torsional spring arm or damping due to rotation arm are provided with and connection seat upper joint hole shape, position, measure-alike bolt connecting hole, pass through bolton.

Main damping and fine setting damping module are detachable, have the damping dynamic shock absorber that main damping and fine setting damping module are installed, and dereliction damping and fine setting damping module on the non-damped dynamic vibration absorber.

The fine tuning structure of spring, damping is arranged between lever underarm, the lever upper arm, and lever underarm and lever upper arm are provided with sliding-groove, and the fine tuning structure of spring, damping is fixed by locking wheel and spring bolt and slided in sliding-groove; Torsional spring or damping structure are arranged on torsional spring arm, the damping due to rotation arm.

The quality adjustable structure is comprised of pallet, locating stud and mass block; Pallet is provided with locating stud, and its position and geomery are fixed; Mass block has the attachment hole of same position and geomery.。

Advantage and effect: this dynamic shock absorber under different installation conditionss, only need to provide the connection seat dimensional parameters with the base of the identical form and position tolerance of connection seat to get final product, and has greatly improved the portability of vibration damper.And this vibration damper is with each function modoularization, select different modules according to different situations, can not only realize the conversion of damping-undamped damper type, and with quality, damping and spring ginsengization, satisfy the demand in the parameter of different condition downward modulation vibration-damper itself.Use lever principle, dynamic shock absorber has spring, damping fine tuning structure, can cooperate main spring, main damping that whole dynamic shock absorber parameter is regulated, and satisfies actual requirement of engineering, reaches effectiveness in vibration suppression.Quality adjustment adopts the mass block superposition principle, in a fixed step size scope, can satisfy the continuous adjustable demand of quality.

Description of drawings:

Fig. 1 is the non-damped dynamic vibration absorber mathematical model;

Fig. 2 is non-damped dynamic vibration absorber amplitude response curve;

Fig. 3 is for there being damping dynamic shock absorber mathematical model;

Fig. 4 for have the damping power vibration damping to different damping than device amplitude response curve;

Fig. 5 is for having the damping dynamic shock absorber to given design method amplitude response curve comparison figure;

Fig. 6 is spring, damping equivalent mass figure;

Fig. 7 is the plan view of dynamic shock absorber;

Fig. 8 is the dynamic shock absorber normal axomometric drawing;

Fig. 9 is the dynamic shock absorber fine tuning structure, schematic representation when spring (damping) is vertical;

Figure 10 is the dynamic shock absorber fine tuning structure, the schematic representation when spring (damping) tilts;

Figure 11 is for adopting torsional spring, damping dynamic shock absorber plan view;

Figure 12 is the connection seat plan view;

Figure 13 is that dynamic shock absorber is at the connection diagram that is applied on the pipeline;

Figure 14 is the dynamic shock absorber figure that is connected in parallel.

In the accompanying drawing, the part that each label is corresponding or structure title are as follows:

1, base; 2, connection seat; 3, hinged-support; 4, lever underarm; 5, coupling shaft; 6, lever upper arm; 7, locking wheel; 8, fine setting spring; 9, contiguous block; 10, locating stud; 11, locking nut; 12, guide rail; 13, mass block; 14, pallet; 15, main spring; 16, sliding-groove; 17, fine setting damping; 18, main damping; 19, spring bolt; 20, torsional spring arm; 21, force-transmitting block; 22, rotation damper; 23, damping due to rotation arm; 24, hole in parallel; 25, connecting hole; 26, carry piece; 27, locking belt; 28, pipeline; 29 and sell through joint efforts.

SpecificallyMode of execution:

A kind of dynamic shock absorber, mainly by base 1, connection seat 2, hinged-support 3, lever underarm 4, lever upper arm 6, fine setting spring 8, guide rail 12, mass block 13, pallet 14, main spring 15, fine setting damping 17, main damping 18, hole in parallel 24 form.

The model of non-damped dynamic vibration absorber can be simplified to Fig. 1.Original system is simplified to k ₁, m ₁, vibration damper is simplified to k ₂, m ₂, the system vibration frequency is ω.Then original single degree of freedom system has become two degree freedom system.Can get motion equation according to system architecture and be this moment:

$\left[\begin{array}{cc}{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">m</figure-callout>}}_1& 0\\ 0& m_2\end{array}\right]\left\{\begin{array}{c}{\stackrel{\&CenterDot;\&CenterDot;}{x}}_1\\ {\stackrel{\&CenterDot;\&CenterDot;}{x}}_2\end{array}\right\}+\left[\begin{array}{cc}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">k</figure-callout>}}_1+k_2& -k_2\\ -k_2& k_2\end{array}\right]\left\{\begin{array}{c}{x}_1\\ x_2\end{array}\right\}=\left\{\begin{array}{c}\mathrm{<figure-callout\; id="0"\; label="F"\; filenames="HDA00003142342400013.png,HDA00003142342400051.png"\; state="\{\{state\}\}">F</figure-callout>}\\ 0\end{array}\right\}\sin \mathrm{\&omega;t}---\left(1\right)$

According to equation (1), obtain its solution with complex function and be:

${\stackrel{\&OverBar;}{X}}_1=\frac{[1-{\left(\frac{\mathrm{\&omega;}}{{\mathrm{\&omega;}}_2}\right)}^2]X_0}{[1+\mathrm{\&mu;}{\left(\frac{{\mathrm{\&omega;}}_2}{{\mathrm{\&omega;}}_1}\right)}^2-{\left(\frac{\mathrm{\&omega;}}{{\mathrm{\&omega;}}_1}\right)}^2][1-{\left(\frac{\mathrm{\&omega;}}{{\mathrm{\&omega;}}_2}\right)}^2]-\mathrm{\&mu;}{\left(\frac{\mathrm{\&omega;}}{{\mathrm{\&omega;}}_1}\right)}^2}---\left(2\right)$

${\stackrel{\&OverBar;}{X}}_2=\frac{X_0}{[1+\mathrm{\&mu;}{\left(\frac{{\mathrm{\&omega;}}_2}{{\mathrm{\&omega;}}_1}\right)}^2-{\left(\frac{\mathrm{\&omega;}}{{\mathrm{\&omega;}}_1}\right)}^2][1-{\left(\frac{\mathrm{\&omega;}}{{\mathrm{\&omega;}}_2}\right)}^2]-\mathrm{\&mu;}{\left(\frac{\mathrm{\&omega;}}{{\mathrm{\&omega;}}_1}\right)}^2}$

Wherein:

The former vibration system rigidity of m1---former vibration plastid quality k1---

M2---vibration damper mass of vibration k2---vibration damper is joined the rigidity of shaking

C---vibration damper is joined the damping of shaking (when considering damping) x ₁---the displacement of former vibration plastid

x ₂---vibration damper is joined the plastid displacement F that shakes ₁---former vibration plastid excitation force

ω---vibration plastid excited frequency

---the main system natural frequency;

X ₀=F/k ₁---the equivalent static displacement of main system;

---the vibration damper natural frequency;

μ=m ₂/ m ₁---vibration damper quality and main system mass ratio.

According to as above equation, as ω=ω ₂During ± Δ ω, main system quality amplitude is close to zero, and its amplitude curve as shown in Figure 2.

Damping dynamic shock absorber simplified model such as Fig. 3 are arranged.Original system is simplified to k ₁, m ₁, vibration damper is simplified to k ₂, m ₂, c ₂, the system vibration frequency is ω.Can get motion equation according to system architecture and be this moment:

$\left[\begin{array}{cc}{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">m</figure-callout>}}_1& 0\\ 0& m_2\end{array}\right]\left\{\begin{array}{c}{\stackrel{\&CenterDot;\&CenterDot;}{x}}_1\\ {\stackrel{\&CenterDot;\&CenterDot;}{x}}_2\end{array}\right\}\left[\begin{array}{cc}c& -c\\ -c& c\end{array}\right]+\left\{\begin{array}{c}{\stackrel{\&CenterDot;}{x}}_1\\ {\stackrel{\&CenterDot;}{x}}_2\end{array}\right\}+\left[\begin{array}{cc}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">k</figure-callout>}}_1+k_2& -k_2\\ -k_2& k_2\end{array}\right]\left\{\begin{array}{c}{x}_1\\ x_2\end{array}\right\}=\left\{\begin{array}{c}\mathrm{<figure-callout\; id="0"\; label="F"\; filenames="HDA00003142342400013.png,HDA00003142342400051.png"\; state="\{\{state\}\}">F</figure-callout>}\\ 0\end{array}\right\}\sin \mathrm{\&omega;t}---\left(3\right)$

Solution of equation is:

${\mathrm{<figure-callout\; id="1"\; label="X"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">X</figure-callout>}}_1=\frac{F\sqrt{(k_2-{\mathrm{\&omega;}}^{2}m)+{\mathrm{\&omega;}}^2{c}^2}}{\sqrt{a^2+{\mathrm{<figure-callout\; id="2"\; label="b"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">b</figure-callout>}}^2}}$

(4)

${\mathrm{<figure-callout\; id="2"\; label="X"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">X</figure-callout>}}_2=\frac{\mathrm{<figure-callout\; id="2"\; label="F\; k"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">F</figure-callout>}\sqrt{k_{}}\sqrt{{}_2+{\mathrm{\&omega;}}^2{c}^2}}{\sqrt{a^2+{\mathrm{<figure-callout\; id="2"\; label="b"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">b</figure-callout>}}^2}}$

In the formula, $\begin{array}{c}a=(k_1-{\mathrm{\&omega;}}^2{m}_1)(k_2-{\mathrm{\&omega;}}^2{m}_2)-{\mathrm{\&omega;}}^2{k}_2{m}_2\\ b=\mathrm{\&omega;c}(k_1-{\mathrm{\&omega;}}^2{m}_1-{\mathrm{\&omega;}}^2{m}_2)\end{array}$

Introduce following symbol:

$\frac{\mathrm{<figure-callout\; id="1"\; label="F\; k"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">F</figure-callout>}}{k_{}}={\mathrm{<figure-callout\; id="0"\; label="X"\; filenames="HDA00003142342400013.png,HDA00003142342400051.png"\; state="\{\{state\}\}">X</figure-callout>}}_0,$ ${\mathrm{\&omega;}}_1=\sqrt{\frac{k_1}{{\mathrm{<figure-callout\; id="1"\; label="m"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">m</figure-callout>}}_1}},$ $\mathrm{\&mu;}=\frac{m_1}{{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">m</figure-callout>}}_2},$ $\mathrm{\&delta;}=\frac{{\mathrm{\&omega;}}_1}{{\mathrm{\&omega;}}_2},$ $r=\frac{\mathrm{\&omega;}}{{\mathrm{\&omega;}}_1},$ $\mathrm{\&zeta;}=\frac{c}{2{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">m</figure-callout>}}_2{\mathrm{\&omega;}}_1}$

System's amplitude is write as Dimensionless Form, is had:

$\frac{{\mathrm{<figure-callout\; id="1"\; label="X"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">X</figure-callout>}}_1^2}{{\mathrm{<figure-callout\; id="0"\; label="X"\; filenames="HDA00003142342400013.png,HDA00003142342400051.png"\; state="\{\{state\}\}">X</figure-callout>}}_0^2}=\frac{{({\mathrm{\&delta;}}^2-r^2)}^2+4{\mathrm{\&zeta;}}^2{r}^2}{[(1-r^2)({\mathrm{\&delta;}}^2-r^2)-{\mathrm{\&mu;<figure-callout\; id="2"\; label="r"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">r</figure-callout>}}^2{\mathrm{\&delta;}}^2{]}^2+4{\mathrm{\&zeta;}}^2{r}^2{(1-r^2-{\mathrm{\&mu;r}}^2)}^2}---\left(5\right)$

According to following formula, damping dynamic shock absorber amplitude curve such as Fig. 4 have been drawn.We see that all response curves all meet at S and T point in the drawings.The r value that S and T point are corresponding can be tried to achieve by the response curve of two different damping values.The vibration amplitude that is exactly when ζ=0 and ζ=∞ of most convenient equates to obtain, that is:

$\frac{{\mathrm{\&delta;}}^2-r^2}{(1-r^2)({\mathrm{\&delta;}}^2-r^2)-{\mathrm{\&mu;<figure-callout\; id="2"\; label="r"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">r</figure-callout>}}^2{\mathrm{\&delta;}}^2}=\frac{\&PlusMinus;1}{1-r^2-{\mathrm{\&mu;r}}^2}---\left(6\right)$

(6) get positive sign, μ r is arranged ⁴=0, r=0, this is not the result that we want; Get negative sign, have:

$r^4-2{\mathrm{<figure-callout\; id="2"\; label="r"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">r</figure-callout>}}^2\frac{1+{\mathrm{\&delta;}}^2+\mathrm{\&mu;}{\mathrm{\&delta;}}^2}{2+\mathrm{\&mu;}}+\frac{2{\mathrm{\&delta;}}^2}{2+\mathrm{\&mu;}}=0---\left(7\right)$

Try to achieve r corresponding to S, T point by (7) _S, r _TRepresentation.Carry it into the damping value response equation, obtain:

$\frac{X_{1\mathrm{<figure-callout\; id="0"\; label="S\; X"\; filenames="HDA00003142342400013.png,HDA00003142342400051.png"\; state="\{\{state\}\}">S</figure-callout>}}}{X_{}}=\frac{1}{1-r_S^2-\mathrm{\&mu;}{\mathrm{<figure-callout\; id="2"\; label="r\; S"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">r</figure-callout>}}_S^{}}$

(8)

$\frac{X_{1\mathrm{<figure-callout\; id="0"\; label="T\; X"\; filenames="HDA00003142342400013.png,HDA00003142342400051.png"\; state="\{\{state\}\}">T</figure-callout>}}}{X_{}}=\frac{1}{1-r_T^2-\mathrm{\&mu;}{\mathrm{<figure-callout\; id="2"\; label="r\; T"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">r</figure-callout>}}_T^{}}$

For engineering problem, as long as make X ₁Just passable in the permitted value scope, not necessarily to reach zero.So with X ₁Be designed to certain response curve maximum value, and make X _1T=X _1SGet final product.By X _1T=X _1S:

$\mathrm{\&delta;}=\frac{1}{1+\mathrm{\&mu;}}---\left(9\right)$

Bring formula (7) into:

Thereby have:

$\frac{X_{1\mathrm{<figure-callout\; id="0"\; label="S\; X"\; filenames="HDA00003142342400013.png,HDA00003142342400051.png"\; state="\{\{state\}\}">S</figure-callout>}}}{X_{}}=\frac{X_{1\mathrm{<figure-callout\; id="0"\; label="T\; X"\; filenames="HDA00003142342400013.png,HDA00003142342400051.png"\; state="\{\{state\}\}">T</figure-callout>}}}{X_{}}=\sqrt{\frac{2+\mathrm{\&mu;}}{\mathrm{\&mu;}}}---\left(11\right)$

So just determine the μ value, and then determined vibration damper quality m ₂Bring μ into (9) and namely obtain the δ value, thereby determined ω ₂Value, thus determined spring constant k ₂Determine at last c.In order to make X _1TAnd X _1SBe the response curve maximum value, make it that horizontal tangent be arranged, thereby obtain the ζ value, but X _1TAnd X _1Sζ value and unequal, so average:

$\mathrm{\&zeta;}=\sqrt{\frac{3\mathrm{\&mu;}}{8(1+\mathrm{\&mu;})}}---\left(12\right)$

Can determine vibration damper m according to above method ₂, k ₂, c parameter.Fig. 5 is different parameters has the damping dynamic shock absorber to system's amplitude impact, and we see that the calculated value of given design method (shown in the dotted line) is controlled at amplitude below the expected value, realistic requirement.

Dynamic shock absorber base 1 and connection seat 2 are connected with hinged-support and are connected with bolt, according to different installation conditionss, are implemented in the installation requirements of different surfaces situation.Under different operating modes, only need to make the base 1 of corresponding requirements, and get final product in the identical shape of base 1 processing and in parallel 2 and the Bolt Connection hole 25 of position.Base 1 and connection seat 2 and hinged-support 3 connect by bolton, have greatly improved the portability of dynamic shock absorber.Changing in the installation conditions situation, do not need to redesign structure, only need provide the base 1 of response to get final product, saved cost and time.

Spring becomes modular construction with damping design, hinged-support 3, torsional spring arm 20 or damping due to rotation arm 23 are provided with the bolt connecting hole with connection seat 2 upper joint holes, 25 same positions and geomery, after choosing corresponding module and parameter, only needs and base 1 and connection seat 2 are locked together and are got final product.Such structure can not only be changed module as the case may be under different situations, realize the switching of dissimilar springs, damping module; Also make the design simplification of vibration damper, shortened whole development to the practical time.By such structure, can also realize the switching between damping dynamic shock absorber and the non-damped dynamic vibration absorber.Have the damping dynamic shock absorber that main damping 18 and fine setting damping 17 structures will be installed, and non-damped dynamic vibration absorber is not installed and is stated module and get final product.Equally, main damping 18 also is to link to each other with pallet 14 with connection seat 2 by bearing pin or coupling shaft, is easy for installation and removal.

Dynamic shock absorber spring, damping fine tuning structure are by lever underarm 4, lever upper arm 6 and fine setting damping 17 and 8 one-tenth of fine setting cluster spring.Lever underarm 4, lever upper arm 6 are provided with sliding-groove 16, and spring bolt 19 can wherein slide again; The length of lever arm of force can be by the determining positions of spring bolt 19 in sliding-groove 16; After determining the position, with locking wheel 7 rotational locks, namely finished the location of spring bolt 19 in sliding-groove 16; For torsional spring, damping structure, sliding-groove 16 is arranged on torsional spring arm 20, damping due to rotation arm 23 and the pallet 14, with the position of adjusted spring bolt 19, so also can realize above-mentioned functions.

Fig. 9 is the given method schematic representation of spring, damping fine tuning structure equivalent parameters, the given method of fine tuning structure is suc as formula (13)-(20), the given method of torsional spring shown in Figure 10, damping fine tuning structure equivalent parameters, as long as coordinate x, v replaces to angle θ and the ω angular acceleration gets final product.For other similar structure, as long as take generalized coordinates system, suc as formula the equivalent parameters that (13)-(20) can meet with a response.

The dynamic shock absorber fine tuning structure adopts lever principle, comes the parameter of Regulation spring and damping according to the difference of the arm of force.Structure as shown in Figure 7, spring equivalent stiffness and the given method of damping equivalent parameters are as follows.Such as Fig. 9, dynamic shock absorber is in when work, and parameter c is constantly to change, and is taken at the equilibrium position here and is spring or the damping situation when vertical as force analysis.If spring is vertically placed, computational methods are comparatively simple.If lever (4), (6) arm lengths are l, spring bolt (19) is a to the length of lever coupling shaft (5), coupling shaft (5) displacement that links to each other with contiguous block (9) is x, speed is v, and spring bolt (19) displacement is x ', and speed is v ', spring rate is k, damping size c, equivalent spring rigidity is k ', equivalent c '.

For spring:

$x^{\&prime;}=\frac{l-a}{l}x---\left(13\right)$

(k'·x)·l＝(k·x')·(l-a)

Namely

$k^{\&prime;}={\left(\frac{l-a}{l}\right)}^{2}k---\left(14\right)$

For damping:

$v^{\&prime;}=\frac{l-a}{l}v---\left(15\right)$

(c'·v)·l＝(c·v')·(l-a)

Namely

$c^{\&prime;}={\left(\frac{l-a}{l}\right)}^{2}c---\left(16\right)$

If when being in the equilibrium position, spring, damping slant setting such as Figure 10, have so for spring:

$\mathrm{\&theta;}=\arctan \frac{d}{b-a}---\left(17\right)$

The displacement of spring action point is:

$x^{\&prime;}=\frac{l-a}{l}x---\left(18\right)$

The spring actual displacement is:

x″＝x'·sinθ (19)

By the mechanical equation formula:

(k'·x)·l＝(k·x″)·sinθ·(l-a)

Equivalent stiffness is:

$k^{\&prime;}=k\frac{{(l-a)}^2}{{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">l</figure-callout>}}^2}{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\arctan \frac{d}{b-a}$

In like manner equivalent damping is:

$c^{\&prime;}=c\frac{{(l-a)}^2}{{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">l</figure-callout>}}^2}{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00003142342400013.png,HDA00003142342400032.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\arctan \frac{d}{b-a}---\left(20\right)$

The equivalent mass of linear springs and damping such as Fig. 6:

The quality of spring is m, sets up such as the figure system of coordinates, and be that the indication speed at x place is x ' at coordinate, establish whole spring energy less than dissipation, the maximum kinetic energy that has of spring is so:

$T={\&Integral;}_0^{\mathrm{<figure-callout\; id="1"\; label="l"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">l</figure-callout>}}\frac{1}{2}\&CenterDot;{(\frac{x}{l}\&CenterDot;x^{\&prime;})}^2\&CenterDot;\left(\frac{m}{l}\right)\mathrm{dx}=\frac{1}{6}m{x}^{\&prime;2}=\frac{1}{2}\&CenterDot;\left(\frac{1}{3}m\right)\&CenterDot;x^{\&prime;2}---\left(21\right)$

Obviously, the equivalent mass of spring is

Damping mass is m ', sets up such as the figure system of coordinates, and in the t moment, coordinate is that the indication speed at x place is x ', so damping have can for:

$T={\&Integral;}_0^{\mathrm{<figure-callout\; id="1"\; label="l"\; filenames="HDA00003142342400032.png,HDA00003142342400041.png"\; state="\{\{state\}\}">l</figure-callout>}}\frac{1}{2}\&CenterDot;{(\frac{x}{l}\&CenterDot;x^{\&prime;})}^2\&CenterDot;\left(\frac{m^{\&prime;}}{l}\right)\mathrm{dx}=\frac{1}{6}{m}^{\&prime;}{x}^{\&prime;2}=\frac{1}{2}\&CenterDot;\left(\frac{1}{3}{m}^{\&prime;}\right)\&CenterDot;x^{\&prime;2}---\left(22\right)$

Obviously, the equivalent mass of spring is

As mentioned above, we can be by changing parameter a, and b, d, l regulate the equivalent spring rigidity of fine tuning structure and the parameter that the damping size changes whole system.

The quality of dynamic shock absorber has adjustable structure, and pallet 14 is provided with locating stud 10, and its shape and position dimension are fixed; Mass block 13 has same structure; Mass block 13 is designed to different sizes such as balance weights, and in a fixed step size situation, quality is adjustable continuously, can according to as above the given method quality of regulation of equivalent parameters is big or small, satisfy the operating mode needs like this.

If the parameter that the relatively selected dynamic shock absorber of actual conditions needs is excessive, directly select single dynamic shock absorber can not meet the demands or make the vibration damper hydraulic performance decline, can come the realization demand by the dynamic shock absorber parallel connection, will guarantee when in parallel that the module of dynamic shock absorber and the parameter of response select identical.Have hole 24 in parallel on the pallet 14,14 on different pallets can by and sell through joint efforts and 29 connect.Because two power vibration damping motion conditions are identical, and selling through joint efforts 29, mainly to play maintenance vibration damper amplitude phase place consistent, so namely reaches above-mentioned requirements.

Non-damped dynamic vibration absorber has parameter and regulates special function, when not loading damping module, is the undamped vibration damper when main spring 15 and fine setting spring 8 module only are housed.Under the actual conditions, according to parameter request, select less than and near the main spring 15 of calculating spring rate; Fine setting spring 8 selects parameter to be larger than calculated rigidity and main spring 15 differences, calculates the position of spring bolt 19 in sliding-groove 16 in order to upper algorithm, by locking wheel spring bolt 19 lockings is got final product; The calculating of quality is same, and as above method is considered vibration damper to system's associated mass, calculate again the calculated mass of vibration damper mass block 13 according to above algorithm, cut the associated mass that vibration damper brings to system, be installed in by adjusting and do the size that dish 14 is improved quality piece 13, satisfy quality requirement.

Have the damping dynamic shock absorber to have equally the univers parameter regulatory function, main spring 15, main damping 18 can be according to the parameter demands, select parameter value be less than calculated value and near the damping of calculated value size and spring fitting pallet 14 and and connection seat 2 between; Fine tuning structure damping 17 and fine setting spring 8 select numerical value to be slightly larger than spring and the damper of the difference of calculated value and main spring 15 and main damping 18, draw each spring bolt 19 position in sliding-groove 16 in order to the given method of upper equivalent parameters, by locking wheel spring bolt 19 lockings are got final product; Identical with the undamped absorber designing, do not give unnecessary details.

Claims (6)

1. adjustable dynamic shock absorber of modularization parameter, it is characterized in that: this dynamic shock absorber is mainly by base (1), connection seat (2), hinged-support (3), lever underarm (4), lever upper arm (6), fine setting spring (8), guide rail (12), and mass block (13), pallet (14), main spring (15), fine setting damping (17), main damping (18), hole in parallel (24) form; Base (1) is connected with bolt with connection seat (2), to realize the installation requirements of different surfaces situation; Hinged-support (3) is connected on the connection seat (2) with bolt; Spring and damping have modular construction, and lever underarm (4) links to each other by coupling shaft (5) with lever upper arm (6), are fixed on the hinged-support (3), to realize the fine setting of damping and spring parameter; Pallet (14) is hinged on the lever upper arm (6) by coupling shaft (5) through contiguous block (9); The fixing hole of size is arranged in the mass block (13), cooperatively interact with pallet (14), be fixed on the pallet (14) by lock bolt, mass parameter is regulated; Pallet (14) is provided with slideway, can form sliding pair with guide rail (12), and pallet (14) is slided along fixed-direction; Also be provided with main damping (18) and main spring (15) coupling arrangement on the pallet (14), connect with main damping (18) and main spring (15); Connection seat (2) is provided with coupling arrangement equally, connects with main damping (18) and main spring (15); Pallet (14) has and sells through joint efforts (29), realizes being connected in parallel of dynamic shock absorber.

2. the adjustable dynamic shock absorber of modularization parameter according to claim 1, it is characterized in that: base (1) and connection seat (2) and hinged-support (3) are provided with the fixing connecting hole (25) of size and position, by bolton, to install at different surfaces.

3. the adjustable dynamic shock absorber of modularization parameter according to claim 1, it is characterized in that: spring and damping have modular construction, can select dissimilar being connected on the hinged-support (3); Lever underarm (4), torsional spring arm (20) or damping due to rotation arm (23) are provided with and connection seat (2) upper joint hole (25) shape, position, measure-alike bolt connecting hole, pass through bolton.

4. the adjustable dynamic shock absorber of modularization parameter according to claim 1, it is characterized in that: main damping (18) and fine setting damping (17) module are detachable, there is the damping dynamic shock absorber that main damping (18) and fine setting damping (17) module are installed, and dereliction damping (18) and finely tune damping (17) module on the non-damped dynamic vibration absorber.

5. according to claim 1 or the adjustable dynamic shock absorber of 3 described modularization parameters, it is characterized in that: the fine tuning structure of spring, damping is arranged between lever underarm (4), the lever upper arm (6), lever underarm (4) and lever upper arm (6) are provided with sliding-groove (16), and the fine tuning structure of spring, damping is by locking wheel (7) and spring bolt (19) is fixing and slip in sliding-groove (16); Torsional spring or damping structure are arranged on torsional spring arm (20), the damping due to rotation arm (23).

6. the adjustable dynamic shock absorber of modularization parameter according to claim 1, it is characterized in that: the quality adjustable structure is comprised of pallet (14), locating stud (10) and mass block (13); Pallet (14) is provided with locating stud (10), and its position and geomery are fixed; Mass block (13) has the attachment hole of same position and geomery.

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