CN101680439B - Linear compressor - Google Patents

Abstract

The present invention provides a linear compressor having an elastic body capable of reducing vibration transferred to a shell due to a motion of a moving part. The linear compressor includes a shell defining a hermetic space, a stationary part installed in the shell and having a mass of Mb, a moving part reciprocating linearly inside the stationary part at a frequency of omega to compress a fluid, and having a mass of Ma, a first elastic body having both ends supported on the moving part and the shell respectively, and having an spring constant of ka, a second elastic body having both ends supported on the shell and the stationary part respectively, and having an spring constant of kb, and a third elastic body having both ends supported on the stationary part and the moving part respectively, and having an spring constant of kc. The frequency omega satisfies omega2 > (ka /Ma). In the above configuration, the spring constant kc of the third elastic body is always a positive number, so that the third elastic body can be implemented with a mechanical elastic body more easily designed and controlled than a gas elastic body.

Description

Linear compressor

Technical field

The present invention relates to a kind of linear compressor, more specifically, relate to a kind of elastomeric linear compressor that stops shell to vibrate that has owing to the motion of motion parts.

Background technique

Usually, compressor is to receive from compressing mechanical device with rising pressure such as the power of power generation arrangements such as motor or turbo machine and to air, refrigeration agent or various working gas.Compressor has been widely used in such as in the household electric appliance such as refrigerator and air-conditioning or be used for whole industry.

Compressor roughly is divided into reciprocal compressor, rotary compressor and scroll compressor, in described reciprocal compressor, between piston and cylinder body, be limited with working gas and be drawn into its neutralization from wherein discharging the compression volume of working gas, and described piston carries out straight reciprocating motion with compressed refrigerant in described cylinder body, in described rotary compressor, between the roller of off-centre rotation and cylinder body, be limited with working gas and be drawn into its neutralization from wherein discharging the compression volume of working gas, and described roller rotates with compressed refrigerant along the inwall of described cylinder body is eccentric, and in described scroll compressor, between moving scroll and fixed scroll, be limited with working gas and be drawn into its neutralization from wherein discharging the compression volume of working gas, and described moving scroll along described fixed scroll disc spins with compressed refrigerant.

Recently, obtained develop actively at reciprocal compressor cathetus compressor.Because piston is attached directly to the linear reciprocating drive motor, so linear compressor can improve compression efficiency and simplified structure under the situation that does not cause mechanical loss because of movement conversion.

Generally speaking, in linear compressor, piston carries out straight reciprocating motion by the linear electric motor in the can in cylinder body, thereby refrigeration agent is sucked, compresses and discharges.In linear electric motor, permanent magnet is placed between inner stator and the external stator, makes described permanent magnet to be activated under the effect of mutual electromagnetic power and carries out straight reciprocating motion.Because permanent magnet is to be activated being connected under the state of piston, so described piston carries out straight reciprocating motion in cylinder body, thereby refrigeration agent is sucked, compresses and discharges.

Here, when piston expectedly carried out straight reciprocating motion by the driving of motor, other parts in the shell except elastomer did not carry out desired movement.Therefore, hereinafter, piston and be attached to described piston and be called motion parts with the parts that carry out straight reciprocating motion in company with described piston, and the parts except motion parts are called stationary part.Stationary part and motion parts are attached to shell in the enclosure by means of elastomer.Hereinafter, the vibration system of linear compressor will be interpreted as shell, motion parts, stationary part and elastomeric simple structure.

In linear compressor, stationary part is owing to the motion of motion parts is shifted, and power is passed to the shell that is attached to stationary part by elastomer, makes shell vibrate.The vibration of shell is disadvantageous, because it can reduce the stability of linear compressor and cause noise.

Fig. 1 is the view of an example of diagram traditional vertical linear compressor.Motion parts connects by means of elastomer with shell with shell and motion parts with stationary part, stationary part.When motion parts during by motor driving, three elastomers are shifted simultaneously.Here, first elastomer 20 and second elastomer 21 satisfy following relation:

$\frac{M_b}{M_a}=\frac{k_a}{k_b}$

Formula (1)

Here, M _aThe quality of expression motion parts, described motion parts comprises piston 1, actuator 4 and magnet structure 5, and M _bThe quality of expression stationary part, described stationary part comprises cylinder body 2, cylinder seat 2a and cylinder cap 3.

In addition, the 3rd elastomer 22 that is included in the linear compressor is by motion parts being attached to stationary part and described motion parts is resonated the member of the efficient that improves linear compressor.Yet, satisfy under the state of formula (1) k at first elastomer 20 and second elastomer 21 _cIt must be negative and make the 3rd elastomer 22 can satisfy resonance condition.Thereby, can't use to be the most widely-used and easy controlled elastomeric mechanical spring.

Summary of the invention

Technical problem

An object of the present invention is to provide a kind of linear compressor, described linear compressor has the elastomer that can reduce to be passed to owing to the motion of motion parts the vibration of shell.

Another object of the present invention provides a kind of linear compressor, and wherein, the elastomer that is used to reduce to vibrate is all realized with the mechanical elasticity body.

Another purpose of the present invention provides a kind of linear compressor, and wherein, motion parts is so that be passed to the frequency along continuous straight runs motion of the minimum vibration of shell owing to the motion of motion parts.

Technological scheme

According to the present invention, a kind of linear compressor is provided, comprising: shell, described shell limits seal space; Stationary part, described stationary part are installed in the described shell and have mass M _bMotion parts, described motion parts carries out straight reciprocating motion with compressed fluid with frequencies omega in described stationary part, and described motion parts has mass M _aFirst elastomer, the described first elastomeric two ends are supported on described motion parts and the described shell respectively and have spring constant k _aSecond elastomer, the described second elastomeric two ends are supported on described shell and the described stationary part respectively and have spring constant k _bAnd the 3rd elastomer, the described the 3rd elastomeric two ends are supported on described stationary part and the described motion parts respectively and have spring constant k _c, wherein, described frequencies omega satisfies

${\mathrm{\ω}}^2>\frac{k_a}{M_a}$

In said structure, the 3rd elastomeric spring constant k _cAlways positive number makes the 3rd elastomer to realize by enough mechanical elasticity bodies than easier design of elasticity of gases body and control.

According to another aspect of the present invention, described first elastomer and described second elastomer satisfy

$\frac{k_b}{k_a}=\frac{M_b}{M_b}.$

In said structure, the power that is passed to shell owing to the motion of motion parts can be cancelled, and has reduced the vibration of shell thus.

According to a further aspect of the invention, the described the 3rd elastomeric spring constant k _cSatisfy

$k_c=\frac{M_a}{M_{a+M_b}}(M_a.{\mathrm{\ω}}^2-k_a)$

Thereby make described motion parts resonance.In said structure, linear compressor can be worked under resonance condition.

According to a further aspect of the invention, the described frequencies omega resonant frequency that is described motion parts

According to a further aspect of the invention, described the 3rd elastomer is the mechanical elasticity body.

In addition,, provide a kind of linear compressor, having comprised according to the present invention: shell, described shell limits seal space; Stationary part, described stationary part are installed in the described shell and have mass M _bMotion parts, described motion parts carries out straight reciprocating motion with compressed fluid with frequencies omega in described stationary part, and described motion parts has mass M _aFirst elastomer, the described first elastomeric two ends are supported on described motion parts and the described shell respectively and have spring constant k _aSecond elastomer, the described second elastomeric two ends are supported on described shell and the described stationary part respectively and have spring constant k _bAnd the 3rd elastomer, the described the 3rd elastomeric two ends are supported on described stationary part and the described motion parts respectively and have spring constant k _c, wherein, the described the 3rd elastomeric spring constant k _cSatisfy

$k_c=\frac{M_a}{M_{a+M_b}}(M_a{.\mathrm{\ω}}^2-k_a).$

According to another aspect of the present invention, described first elastomer and described second elastomer satisfy

$\frac{k_b}{k_a}=\frac{M_b}{M_a}.$

Technique effect

According to the present invention, in linear compressor, two ends are supported on stationary part and the motion parts respectively and apply restoring force and the 3rd elastomeric spring constant that makes motion parts to work can be positive number under resonance conditions.

In addition, according to the present invention, in linear compressor, frequency of okperation is adjusted to and makes the 3rd elastomeric spring constant can be positive number.

And according to the present invention, in linear compressor, the transmission power that is passed to shell is offset to reduce noise and vibration.

Further, according to the present invention, in linear compressor, owing to be arranged so that the elastomeric spring constant that motion parts can be worked is a positive number under resonance condition, elastomer can be realized by enough mechanical springs.

In addition, according to the present invention, in linear compressor, the 3rd elastomer can be realized by enough mechanical springs.When comparing with the situation that the 3rd elastomer is realized with gas spring, this has simplified design, rigidity adjustment and control.

Further, according to the present invention, the transmission power that is passed to shell is offset, and makes linear compressor stably to work.

Description of drawings

Fig. 1 is the view of an example of diagram traditional vertical linear compressor;

Fig. 2 is the view of diagram according to the linear compressor of embodiment of the present invention;

Fig. 3 is the schematic representation of diagram according to the vibration system of the linear compressor of embodiment of the present invention; And

Fig. 4 is the figure that is illustrated in according to the relation between the transmission power of first elastomer in the linear compressor of embodiment of the present invention and the second elastomeric Young's modulus and shell.

Embodiment

Hereinafter, describe in detail with reference to the accompanying drawings according to linear compressor of the present invention.

Fig. 3 is the schematic representation of diagram according to the vibration system of the linear compressor of embodiment of the present invention.

The vibration system of linear compressor comprises shell 11, motion parts 12, stationary part 13, first elastomer 14, second elastomer 15 and the 16 and the 3rd elastomer 17.The variable that is used for explaining vibration system comprises the displacement x of motion parts 12 _a, stationary part 13 displacement x _b, motion parts 12 mass M _a, stationary part 13 mass M _b, first elastomer 14 spring constant k _a, each second elastomer 15 and 16 spring constant 0.5k _b, the 3rd elastomer 17 spring constant K _c, parameter of electric machine L, R, α and V, motor output F _m, first elastomer 14 imposes on the power F of motion parts 12 _a, each second elastomer 15 and 16 imposes on the power 0.5F of stationary part 13 _b, absolute coordinate system N and each unit vector

With

Here, the spring constant k of the 3rd elastomer 17 _cBe to work as the fluid elastic force that is produced when fluid is compressed owing to the motion of motion parts 12 to take the value that calculates into account.That is to say that for convenience's sake, the summation of the spring constant that the spring constant of the 3rd elastomer 17 and compression owing to fluid are produced is expressed as spring constant k _c

Shell 11 has the resonant frequency far above frequency of okperation.Therefore, be under the situation of rigid body vibration system to be made an explanation at supposition shell 11.And, in order to explain the system of motion parts 12, stationary part 13 and electric current, generalized coordinates x _a(t), x _b(t) and q (t) be necessary.

At first, use the kinetic energy T of the vibration system of above-mentioned variable to represent by following formula:

$T=\frac{M_a}{2}{{\stackrel{\&CenterDot;}{x}}_a}^2+M_b{{\stackrel{\&CenterDot;}{x}}_{\mathrm{<figure-callout\; id="2"\; label="b"\; filenames="H200780042846XE00011.png,H200780042846XE00022.png"\; state="\{\{state\}\}">b</figure-callout>}}}^2+\frac{L}{2}{\stackrel{\&CenterDot;}{q}}^2$

In addition, elastic energy V is represented by following formula:

$V=\frac{k_a}{2}{x_a}^2\text{+}\frac{k_c}{2}{(x_b-x_a)}^2+\frac{k_b}{2}{x_b}^2$

In addition, damping can be represented by following formula by R:

$R=\frac{R}{2}{\stackrel{\&CenterDot;}{q}}^2$

Further, virtual work δ W is represented by following formula:

$\mathrm{\&delta;W}=\mathrm{\&alpha;}\&CenterDot;\stackrel{\&CenterDot;}{q}\&CenterDot;(\mathrm{\&delta;}{x}_a-\mathrm{\&delta;}{x}_b)-\mathrm{\&alpha;}({\stackrel{\&CenterDot;}{x}}_a-{\stackrel{\&CenterDot;}{x}}_b)\mathrm{\&delta;q}$

In addition, the Lagrange's equation of vibration system is represented by following formula:

$\frac{d}{\mathrm{dt}}\left(\frac{\&PartialD;T}{\&PartialD;{\stackrel{\&CenterDot;}{p}}_i}\right)-\frac{\&PartialD;T}{\&PartialD;p_i}+\frac{\&PartialD;V}{\&PartialD;p_i}+\frac{\&PartialD;R}{\&PartialD;{\stackrel{\&CenterDot;}{p}}_i}=Q_i$

$Q_i=\frac{\&PartialD;W}{{\&PartialD;x}_i}$

With each energy theorem T, V, R and the δ W substitution Lagrange's equation of above derivation, as follows:

$M_a{\stackrel{\&CenterDot;\&CenterDot;}{x}}_a+(k_a+k_c)\&CenterDot;x_a-k_c\&CenterDot;x_b=\mathrm{\&alpha;}\stackrel{\&CenterDot;}{q}(=F_m)$

Formula (2)

$M_b{\stackrel{\&CenterDot;\&CenterDot;}{x}}_b-k_c\&CenterDot;x_a+(k_b+k_c)\&CenterDot;x_b=-\mathrm{\&alpha;}\stackrel{\&CenterDot;}{q}(=-F_m)$

Formula (3)

$L\stackrel{\&CenterDot;\&CenterDot;}{q}+R\stackrel{\&CenterDot;}{q}+\mathrm{\&alpha;}({\stackrel{\&CenterDot;}{x}}_a-{\stackrel{\&CenterDot;}{x}}_b)=V$

Formula (4)

Above-mentioned formula (2) and (3) are expressed as following determinant:

$\left[\begin{array}{cc}{M}_a& 0\\ 0& M_b\end{array}\right]\left\{\begin{array}{c}{\stackrel{\&CenterDot;\&CenterDot;}{x}}_a\\ {\stackrel{\&CenterDot;\&CenterDot;}{x}}_b\end{array}\right\}+\left[\begin{array}{cc}{k}_a+k_c& -k_c\\ -k_c& k_c+k_b\end{array}\right]\left\{\begin{array}{c}{x}_a\\ x_b\end{array}\right\}=\left\{\begin{array}{c}{F}_m\\ -F_m\end{array}\right\}$

Formula (5)

Instantaneous source F _mSatisfy hamonic function F _m=F ₀e ^JwtTherefore, the displacement x of motion parts 12 and stationary part 13 _aAnd x _bBe represented as hamonic function x respectively _a=X _A0e ^IwtAnd x _b=X _B0e ^IwtCan will be represented as displacement substitution formula (2) and (3) of hamonic function, as follows:

$\left[\begin{array}{cc}{k}_a+k_c-M_a\&CenterDot;{\mathrm{\&omega;}}^2& -k_c\\ -k_c& k_c+k_b-M_b\&CenterDot;{\mathrm{\&omega;}}^2\end{array}\right]\left\{\begin{array}{c}{X}_{a0}\\ {\mathrm{<figure-callout\; id="0"\; label="X\; b"\; filenames="H200780042846XE00022.png"\; state="\{\{state\}\}">X</figure-callout>}}_b\end{array}\right\}=\left\{\begin{array}{c}{F}_0\\ -{\mathrm{<figure-callout\; id="0"\; label="F"\; filenames="H200780042846XE00022.png"\; state="\{\{state\}\}">F</figure-callout>}}_0\end{array}\right\}$

Formula (6)

X _A0And X _B0Can represent by following formula:

$\left\{\begin{array}{c}{X}_{a0}\\ {\mathrm{<figure-callout\; id="0"\; label="X\; b"\; filenames="H200780042846XE00022.png"\; state="\{\{state\}\}">X</figure-callout>}}_b\end{array}\right\}={\left[\begin{array}{cc}{k}_a+k_c-M_a\&CenterDot;{\mathrm{\&omega;}}^2& -k_c\\ -k_c& k_c+k_b-M_b\&CenterDot;{\mathrm{\&omega;}}^2\end{array}\right]}^{-1}\&CenterDot;\left\{\begin{array}{c}{F}_0\\ {-\mathrm{<figure-callout\; id="0"\; label="F"\; filenames="H200780042846XE00022.png"\; state="\{\{state\}\}">F</figure-callout>}}_0\end{array}\right\}$

$=\frac{F_0}{D}\&CenterDot;\left[\begin{array}{cc}{k}_a+k_c-M_a\&CenterDot;{\mathrm{\&omega;}}^2& -k_c\\ {-k}_c& k_c+k_b-M_b\&CenterDot;{\mathrm{\&omega;}}^2\end{array}\right]\&CenterDot;\left\{\begin{array}{c}1\\ -1\end{array}\right\}$

$=\frac{F_0}{D}\&CenterDot;\left\{\begin{array}{c}{k}_b-M_b\&CenterDot;{\mathrm{\&omega;}}^2\\ -k_b+M_b\&CenterDot;{\mathrm{\&omega;}}^2\end{array}\right\}$

Formula (7)

Here, D=(k _a+ k _c-m _aω ²) (k _b+ k _c-m _bω ²)-k _c ²..

The summation Fs that acts on the transmission power on the shell 11 is represented by following formula:

F _s＝(k _a·X _a0+k _b·X _bo)·e ^jwt

Formula (8)

With formula (7) concern substitution formula (8), as follows:

$F_s=(k_a\&CenterDot;\frac{F_0}{D}(k_b-M_b\&CenterDot;{\mathrm{\&omega;}}^2)+k_b\&CenterDot;\frac{F_0}{D}(-k_a+M_a\&CenterDot;{\mathrm{\&omega;}}^2))\&CenterDot;e^{\mathrm{jwt}}$

$=\frac{F_0}{D}(-k_a\&CenterDot;M_b+k_b\&CenterDot;M_a)\&CenterDot;{\mathrm{\&omega;}}^2\&CenterDot;e^{\mathrm{jwt}}$

$=\frac{{\mathrm{<figure-callout\; id="0"\; label="F"\; filenames="H200780042846XE00022.png"\; state="\{\{state\}\}">F</figure-callout>}}_0\&CenterDot;{\mathrm{\&omega;}}^2\&CenterDot;(-k_a\&CenterDot;M_b+k_b\&CenterDot;M_a)}{(k_a+k_c-M_a{\mathrm{\&omega;}}^2)(k_b+k_c-M_b{\mathrm{\&omega;}}^2)-{k_c}^2}{e}^{\mathrm{jwt}}$

Formula (9)

When the power that is passed to shell 11 is cancelled and makes that clean power can be for zero the time, the vibration of shell 11 can be reduced.Molecule is necessary for zero in formula (9), makes the summation F of transmission power _sCan be zero.Because at the duration of work of linear compressor, F ₀With the value of ω always greater than zero, so (k _aM _b+ k _bM _a) be necessary for zero.Therefore, for the transmission power of offsetting shell 11 and reduce vibration, the mass M of motion parts 12 _a, stationary part 13 mass M _b, first elastomer 14 spring constant k _aAnd second elastomer 15 and 16 spring constant k _bMust meet the following conditions:

$\frac{k_b}{k_a}=\frac{M_b}{M_a}$

Formula (10)

And in the linear compressor according to one embodiment of the present invention, the 3rd elastomer 17 must have enough spring constants so that motion parts 12 resonance.As instantaneous source F in formula (2) and (3) _mWhen being zero, can be with the spring constant k of the 3rd elastomer 17 _cBe expressed as following determinant:

$\left[\begin{array}{cc}{M}_a& 0\\ 0& M_b\end{array}\right]\left\{\begin{array}{c}{\stackrel{\&CenterDot;\&CenterDot;}{x}}_a\\ {\stackrel{\&CenterDot;\&CenterDot;}{x}}_b\end{array}\right\}+\left[\begin{array}{cc}{k}_a+k_c& -k_c\\ -k_c& k_c+k_b\end{array}\right]\left\{\begin{array}{c}{x}_a\\ x_b\end{array}\right\}=\left\{\begin{array}{c}0\\ 0\end{array}\right\}$

That is to say, work as relation

{x}＝{X}e ^iwt

When using with following form,

$\left[M\right]\left\{\stackrel{\&CenterDot;\&CenterDot;}{x}\right\}+\left[K\right]\left\{x\right\}=\left\{0\right\}$

Then following formula is set up:

$\left[\begin{array}{cc}{k}_a+k_c-M_a\&CenterDot;{\mathrm{\&omega;}}^2& -k_c\\ -k_c& k_a+k_c-M_b\&CenterDot;{\mathrm{\&omega;}}^2\end{array}\right]\left\{X\right\}=\left\{0\right\}$

Here, the determinant of matrix [A] is necessary for zero, and { X}={0} can have feasible solution to make equation [A].

Therefore, the determinant of [K] is represented as

(k _a+k _c-M _a·ω ²)·(k _c+k _b-M _b·ω ²)-k _c ²＝0

And K _cRepresent by following formula:

$k_c=-\frac{(k_a-M_a\&CenterDot;{\mathrm{\&omega;}}^2)\&CenterDot;(k_b-M_b\&CenterDot;{\mathrm{\&omega;}}^2)}{(k_a-M_a\&CenterDot;{\mathrm{\&omega;}}^2)+(k_b-M_b\&CenterDot;{\mathrm{\&omega;}}^2)}$

$=\frac{M_a}{M_a+M_b}(M_a{\mathrm{\&omega;}}^2-k_a)$

Formula (11)

Work as k _cWhen being positive number, the 3rd elastomer 17 can enoughly be realized such as common mechanical elasticity bodies such as helical springs.Therefore, as substitution k _cDuring＞0 condition,

${\mathrm{\&omega;}}^2>\frac{k_a}{M_a}$

Must be met.In addition, consider the resonance condition of motion parts 12, frequencies omega is necessary for the resonant frequency of motion parts 12

The vibration system of linear compressor is based on that above-mentioned condition simulates.Suppose the mass M of motion parts 12 in the vibration system of linear compressor _aIt is the mass M of 0.6kg and stationary part 13 _bBe 5.0kg.Here, as the spring constant k of first elastomer 14 _aWhen being 1440N/m, satisfy second elastomer 15 of formula (10) and the summation k of 16 Young's modulus _bBe 1440 ^*(5.0/0.6), that is, and 12000N/m.

As the k that satisfies formula (11) _cWhen calculating with above-mentioned condition, k _cBe positive number, make the 3rd elastomer 17 to realize by enough controlled and attainable mechanical springs easily.In the situation of traditional vertical linear compressor, be negative owing to satisfy the 3rd elastomeric spring constant of resonance condition, so the 3rd elastomer can not be realized with mechanical spring.The present invention has overcome this defective of prior art.

Fig. 4 illustrates the k that satisfies formula (7) _aAnd k _bThe figure of analog result.In table 1, respectively to k _aAnd k _bCalculate the feasible transmission power F that is passed to shell 11 _sCan be zero.

Table 1

Situation	k a[N/m]	k b[N/m]
			1	960	8,000
2	1,200	10,000
			3	1,440	12,000
4	1,560	14,000

Here, operating conditions is the M-K resonance condition, and the frequency of okperation of motion parts 12 is 50Hz, calculates k thus _ck _cThe fluid elastic force that is produced when fluid is compressed owing to the motion of motion parts 12 can be taken into account and calculate.And peak value is subjected to the restriction of parameter of electric machine α.

Although described preferred implementation of the present invention; but be to be understood that; the present invention should not be limited to these preferred implementations, but those of ordinary skills can carry out various changes and remodeling in the spirit and scope of the present invention for required protection hereinafter.

Claims (5)

1. linear compressor comprises:

Shell, described shell limits seal space;

Stationary part, described stationary part are installed in the described shell and have mass M _b

Motion parts, described motion parts carries out straight reciprocating motion with compressed fluid with frequencies omega in described stationary part, and described motion parts has mass M _a

First elastomer, the described first elastomeric two ends are supported by described motion parts and described shell respectively and have a spring constant k _a

Second elastomer, the described second elastomeric two ends are supported by described shell and described stationary part respectively and have a spring constant k _bAnd

The 3rd elastomer, the described the 3rd elastomeric two ends are supported by described stationary part and described motion parts respectively and have a spring constant k _c,

Wherein, described frequencies omega satisfies

${\mathrm{\&omega;}}^2>\frac{k_a}{M_a}.$

2. linear compressor as claimed in claim 1, wherein, described first elastomer and described second elastomer satisfy

$\frac{k_b}{k_a}=\frac{M_b}{M_a}.$

3. linear compressor as claimed in claim 1, wherein, the described the 3rd elastomeric spring constant k _cSatisfy

$k_c=\frac{M_a}{M_{a+M_b}}(M_a.{\mathrm{\&omega;}}^2-k_a),$

Thereby make described motion parts resonance.

4. linear compressor as claimed in claim 1, wherein, described frequencies omega is the resonant frequency ω of described motion parts _Cr

5. linear compressor as claimed in claim 1, wherein, described the 3rd elastomer is the mechanical elasticity body.

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