CN104074949B - Elastic interlayer type vibration-reduction gear and the method reducing gear drive error - Google Patents

Abstract

The present invention provides a kind of elastic interlayer type vibration-reduction gear and uses the method reducing gear drive error of this gear.Described elastic interlayer type vibration-reduction gear includes: gear matrix, described gear matrix includes circular body and the equally distributed multiple gear teeth base portions of circumferencial direction along circular body；Involute contour body, the both sides of each in multiple gear teeth base portions are respectively arranged with described involute contour body；With elastic interlayer, described elastic interlayer is arranged between gear teeth base portion and involute contour body in a sealing fashion so that each gear teeth base portion forms gear teeth with the involute contour body of both sides and elastic interlayer.The vibration-reduction gear of the present invention can reduce even eliminate vibration by arranging elastic interlayer, and then reduces the driving error of gear.Additionally, the gear of the present invention is owing to using fabricated structure, if some gear teeth serious wear or infringement, the most only need to change an involute contour body, thus provide cost savings, easy and simple to handle and shortening maintenance time.

Description

Elastic interlayer type vibration-reduction gear and the method reducing gear drive error

Technical field

The present invention relates to gear drive field, more particularly, to a kind of elasticity for reducing gear drive error every Laminar vibration-reduction gear and method.

Background technology

Vibration, noise and comfortableness (NVH) are each big car load manufacture of international automobile industry and parts enterprises concern One of problem.Gear, as the important drive disk assembly of modern automobile industry, is the main vibration source in car running process and noise One of source, the dynamic behavior of gear and service behaviour have important impact to car load.A pair actual meshed gears, can not There is various error with avoiding, such as profile error, base pitch error, central moment error etc., thus make actual engagement process become Different.These variations will make involute gear produce the biggest vibration, dynamic loading and noise, the most seriously shadow in transmission process Ring the transmission quality of gear.The vibration of gear not only affects the failure mode of internal gear, such as: breaking off gear teeth, the flank of tooth Spot corrosion and peeling, tooth face agglutination and tooth root crackle etc., but also the resonance of other system of automobile can be caused, such as brakes And steering, thus the reliability of these systems and the safety of car load are had influence on.The prior art indicate that, car load probably has The failure problems of 40% is the vibration by change speed gear box and noise causes, and each major company has the research and development expense of nearly 30% to consume to exist Solve in the problem of this aspect.

The produced vibration of pinion rotation can directly reflect pinion rotation inhomogeneities, and the transmission to drive system misses Difference, noise important.Therefore, the vibration how reducing gear train is an up gear drive quality, reduces transmission by mistake Difference and an effective way of noise, this also becomes those skilled in the art's urgency technical issues that need to address.

Chinese patent ZL200720185373.6 provides a kind of vibration and noise reducing gear, and this gear is by gear mass, teeth group Becoming, the wheel abdomen between tooth root and fixing hole cylindrical is uniformly distributed and arranges multiple through hole, in through hole, interference fit is equipped with foam Aluminum casting resin.The structure of the vibration and noise reducing gear disclosed in this patent documentation is only suitable for discoid flat gear, and This vibration and noise reducing structure processed complex, effect of vibration and noise reduction is undesirable.

Additionally, existing gear is overall structure.If some gear teeth serious wear or infringement, then need to change Whole gear, thus increase cost and maintenance time is long.In view of the problems referred to above of the prior art, need one processing simple And can more effectively reduce gear and the gear error computational methods of gear drive error.

Summary of the invention

In order to solve the problems referred to above, the present invention provides a kind of elastic interlayer type vibration-reduction gear and uses this gear to reduce tooth The method of wheel driving error.The elastic interlayer type vibration-reduction gear of the present invention can reduce even to eliminate shake by arranging elastic interlayer Dynamic, and then reduce the driving error of gear.

According to an aspect of the present invention, a kind of elastic interlayer type vibration-reduction gear includes: gear matrix, described gear matrix The equally distributed multiple gear teeth base portions of circumferencial direction including circular body with along circular body；Involute contour body, multiple The both sides of each in gear teeth base portion are respectively arranged with described involute contour body and elastic interlayer, and described elastic interlayer is with close Envelope mode is arranged between gear teeth base portion and involute contour body so that each gear teeth base portion and the involute contour body of both sides Gear teeth are formed with elastic interlayer.

Elastic interlayer can be between gear teeth base portion and involute contour body.

Further, elastic interlayer can pass through acrylate AB glue, QN-906AB glue, QN-505AB glue or KEYDAK (KD-340) anoxia glue is between gear teeth base portion and involute contour body.

Alternatively, elastic interlayer can be welded between gear teeth base portion and involute contour body.

Further, during described welding includes laser welding, argon arc welding, plasma weldering, the weldering of infrared wire bonding, vacuum electric bundle Any welding.

Elastic interlayer is made up of elastomeric material.

The rigidity of elastomeric material is in the range of 10E3～10E8N/m.

Elastomeric material can be chliorinated polyvinyl chloride, polymer rubber alloy, aluminium alloy or copper alloy.

Elastic interlayer is sized such that width is transverse tooth thickness 0.01～0.3 times of elastic interlayer, elastic interlayer An a length of fully teeth height.

According to another aspect of the present invention, the above-mentioned elastic interlayer type vibration-reduction gear of a kind of use reduces gear drive error Method comprise the following steps: S1: derive only with the gear drive error computing formula of oscillating component；S2: derive only with The two-freedom kinetics equation of the elastic interlayer type vibration damping driving gear of oscillating component, and obtain driving gear matrix steady state solution Amplitude；S3: by the elastic interlayer material chosen, the amplitude of driving gear matrix steady state solution is reduced and trend towards null value；With S4: set up the two-freedom kinetics equation of elastic interlayer type vibration damping driven gear according to S2 step and S3 step, choose elasticity The steady state solution of elastic interlayer type vibration damping driven gear matrix is reduced and trends towards null value by interlayer material, thus makes according to S1 step Driving error with flexible interlayer type vibration-reduction gear system reduces and trends towards null value.

Step S1 farther includes:

The driving error of elastic interlayer type vibration-reduction gear represents with following formula:

X (t)=R_ppθ₁(t)-R_pgθ₃(t) (1)

Wherein, R_ppAnd R_pgIt is respectively the driving gear in the most intermeshing a pair elastic interlayer type vibration-reduction gear and driven The pitch radius of gear, θ₁(t) and θ₃T () is respectively the angular displacement of the matrix of driving gear and driven gear；

The angular displacement of the matrix of driving gear and driven gear includes the position, angle that the angular displacement at the uniform velocity changed and vibration cause Move, following formula represent:

${\mathrm{\θ}}_{1,3}\left(t\right)={\mathrm{\θ}}_{\mathrm{1,3}}^m+{\mathrm{\θ}}_{\mathrm{1,3}}^p\cos \left({\mathrm{\ω}}_{\mathrm{1,3}}t\right)---\left(2\right)$

Wherein,The angular displacement at the uniform velocity changed for elastic interlayer type vibration damping driving gear and driven gear,For elasticity The angular displacement that interlayer type vibration damping driving gear and driven gear cause due to vibration, ω_1,3Angular velocity and ω for vibration_1,3=2 π n_1,3/ 60, n_1,3For elastic interlayer type vibration damping driving gear and the rotating speed of the matrix of driven gear；

For a pair normal meshed gears there is below equation:

$R_{\mathrm{pp}}{\mathrm{\θ}}_1^m=R_{\mathrm{pg}}{\mathrm{\θ}}_3^m---\left(3\right);$ And

Equation (3) is substituted in formula (1) and obtains gear drive error computing formula (4):

$X\left(t\right)=R_{\mathrm{pp}}{\mathrm{\θ}}_1^p\left(t\right)-R_{\mathrm{pg}}{\mathrm{\θ}}_3^p\left(t\right)---\left(4\right).$

S2 step farther includes:

According to the kinetics equation that dAlembert principle acquisition is following:

$I_1{\stackrel{\·\·}{\mathrm{\θ}}}_1+k_1{\mathrm{\θ}}_1+k_2({\mathrm{\θ}}_1-{\mathrm{\θ}}_2)=T_m+T_p\sin \left({\mathrm{\ω}}_{1}t\right)---\left(5\right)$

$I_2{\stackrel{\·\·}{\mathrm{\θ}}}_2-k_2({\mathrm{\θ}}_1-{\mathrm{\θ}}_2)=T_o---\left(6\right)$

Wherein, θ₁And θ₂It is respectively angular displacement and the angle of involute contour body of elastic interlayer type vibration damping driving gear matrix Displacement；k₁Torsional rigidity for gear matrix；k₂Torsional rigidity for elastic interlayer；T_mAnd T_pIt is respectively pair of engaged gears The moment of resistance that the meshing resistance square at the uniform velocity changed and vibration cause；T_oFor the engagement moment of gear, T_o=F_o×R_Pp,Wherein F_oFor Engagement force；I₁Rotary inertia for driving gear；I₂For involute contour body relative to the rotary inertia of gear centre, this rotation The value of inertia is determined by formula for translation of axis (7):

I₂=mL²+I₂₀ (7)

Wherein, m is the quality of involute contour body, and L is the center of mass point o ' length to gear centre of the involute of profile body Degree, I₂₀For the involute contour body rotary inertia relative to self center of mass point o '.

Further, formula (5) and (6) are carried out following coordinate transform, to eliminate the at the uniform velocity change in formula (5) and (6) Change part:

$({\mathrm{\θ}}_1-\frac{T_m+T_o}{k_1},{\mathrm{\θ}}_2-\frac{T_m{k}_2+T_o(k_1+k_2)}{k_1{k}_2})\→({\mathrm{\θ}}_1^p,{\mathrm{\θ}}_2^p)---\left(8\right);$

Coordinate (8) is substituted in formula (5) and (6) and obtains below equation:

$I_1{\stackrel{\·\·}{\mathrm{\θ}}}_1^p+k_1{\mathrm{\θ}}_1^p+k_2({\mathrm{\θ}}_1^p-{\mathrm{\θ}}_2^p)=T_p\sin \left({\mathrm{\ω}}_{1}t\right)---\left(9\right)$

$I_2{\stackrel{\·\·}{\mathrm{\θ}}}_2^p-k_2({\mathrm{\θ}}_1^p-{\mathrm{\θ}}_2^p)=0---\left(10\right),$

The general solution of equation group is expressed as:

Formula (11) is substituted into formula (9) and (10) and obtains following driving gear matrix and involute contour body steady state solution Amplitude:

Wherein, It is respectively elastic interlayer type vibration damping driving gear and the amplitude of driven gear.

S3 step farther includes: according to known involute contour body relative to the rotary inertia I of gear centre₂And bullet Property interlayer type vibration damping driving gear angular velocity of vibration ω₁Choose elastic interlayer material k₂, make the rigidity of elastic interlayer material meet with Lower equation:

$k_2=I_2{\mathrm{\ω}}_1^2---\left(14\right);$ And

By equation (14) substitution (13) acquisition below equation:

Now, elastic interlayer type vibration damping driving gear is by moment produced by elastomeric materialWith elastic interlayer type Oscillating component moment T of vibration damping driving gear matrix_pEquivalence is reversely cancelled out each other so that according to formula (12), elastic interlayer The oscillating component amplitude of formula vibration damping driving gear matrix is

In step s 4, by the angular displacement of the matrix of elastic interlayer type vibration damping driven gear₃, angular velocity of vibration ω₃And base Torsional rigidity k of body₃Replace θ₁、ω₁And k₁Substitute into formula and equation (5)-(15), thus it is driven to obtain elastic interlayer type vibration damping The oscillating component amplitude of gear matrix is

When meeting formula (16) and (17), obtain the driving error of gear according to gear drive error computing formula (4) For:

Accompanying drawing explanation

The explanation of embodiment will be clearly appeared from by above and other aspect and the feature of the present invention from below in conjunction with accompanying drawing, its In:

Fig. 1 is the mesh schematic representation of the elastic interlayer type vibration-reduction gear of a pair according to the present invention；

Fig. 2 is the signal of the structure of the gear matrix showing elastic interlayer type vibration-reduction gear according to embodiments of the present invention Figure；

Fig. 3 is the enlarged diagram of the involute contour body of elastic interlayer type vibration-reduction gear according to embodiments of the present invention； And

Fig. 4 is the schematic diagram of the elastic interlayer of elastic interlayer type vibration-reduction gear according to embodiments of the present invention.

Detailed description of the invention

Describe illustrative, the non-limiting example of the present invention with reference to the accompanying drawings in detail, carry out according to the present invention Further illustrate.

Fig. 1 shows the mesh schematic representation of the elastic interlayer type vibration-reduction gear of a pair according to the present invention, wherein driving gear 1 It is meshed with driven gear 2.Here, as a example by driving gear 1, describe the elastic interlayer according to the present invention in detail with reference to Fig. 1-4 The structure of formula vibration-reduction gear.

Gear 1 includes gear matrix 10, involute contour body 11 and elastic interlayer 12.Gear matrix 10 includes circular body 13 and equally distributed multiple gear teeth base portions 14 of circumferencial direction along circular body 13.See Fig. 3, in multiple gear teeth base portions 14 The both sides of each be respectively arranged with involute contour body 11.Elastic interlayer 12 be arranged in a sealing fashion gear teeth base portion 14 with Between involute contour body 11 so that each gear teeth base portion 14 is formed with the involute contour body 11 of both sides and elastic interlayer 12 One gear teeth of gear.

Elastic interlayer 12 is made up of elastomeric material.In order to make gear obtain good effectiveness in vibration suppression, the rigidity of elastomeric material Preferably in the range of 10E3～10E8N/m.Elastomeric material can be such as chliorinated polyvinyl chloride, polymer rubber alloy, Aluminium alloy or the material of copper alloy, be merely illustrative at this.According to an example, elastic interlayer 12 is pasted onto gear teeth base portion Between 14 and involute contour body 11.Elastic interlayer 12 can use various adhesive to paste, such as pass through acrylate AB glue, QN-906AB glue, QN-505AB glue or KEYDAK (KD-340) anoxia glue are at described gear teeth base portion and described involute contour Between body.It should be noted that the adhesive that elastic interlayer is used is not limited to this, and any glue commonly used in the art can be used Stick.Alternatively, elastic interlayer 12 can also be welded between gear teeth base portion 14 and involute contour body 11.Such as, described Welding includes that any one of laser welding, argon arc welding, plasma weldering, infrared wire bonding, vacuum electric bundle weldering are welded, and only makees at this Do not represent for example enumerates and be limited to above-mentioned listed welding manner.But, elastic interlayer and gear teeth base portion and involute contour The fit system of body is not limited to this, can use any sealing fit system commonly used in the art.

See Fig. 4, show schematically show the elastic interlayer of the elastic interlayer type vibration-reduction gear according to the present invention.A is bullet Property interlayer width in a circumferential direction, b is the length of elastic interlayer, the length that i.e. elastic interlayer extends to tooth top from tooth root. According to the present invention, being preferably sized so that 0.01～0.3 times that a is transverse tooth thickness of elastic interlayer, b is a fully teeth height.

The gear matrix of the elastic interlayer type vibration-reduction gear according to the present invention primarily serves transmission from the power on power transmission shaft Square effect, and linked together with involute contour body by elastic interlayer, thus form elastic interlayer type vibration-reduction gear.One Gear engages transmitting movement and power by involute contour body with the involute contour body conjugation of another gear.Elastic interlayer It is arranged in a sealing fashion between gear matrix and involute contour body, by vibration isolation material by elastic vibration isolation gear matrix Oscillating component is delivered on involute contour body, thus suppresses the mesh vibration of gear, reduces rotational noise, is particularly suited for height The actuating device of precision.The elastic interlayer type vibration-reduction gear of the present invention uses fabricated structure, can be with material customary in the art Material, processing mode and heat treatment method manufacture gear matrix and profile body.Additionally, due to this fabricated structure, if certain One gear teeth serious wear or infringement, the most only need to change an involute contour body just, without changing whole tooth Wheel, thus provide cost savings, easy and simple to handle and shorten maintenance time.Therefore, gear teeth processing technology is good, applies simple technique Just can complete Hardened gear face and high-precision Gear Processing, thus improve the bearing capacity of actuating device, extend the use of gear pair Life-span.

The elastic interlayer type vibration-reduction gear of the present invention can reduce even eliminate vibration by arranging elastic interlayer, and then fall The driving error of low gear.It follows that explanation is reduced gear drive according to the use elasticity interlayer type vibration-reduction gear of the present invention The method of error.

The method reducing gear drive error according to the present invention comprises the following steps:

S1: derive only with the gear drive error computing formula of oscillating component；

S2: the only two-freedom kinetics equation of elastic interlayer type vibration damping driving gear with oscillating component of deriving, and Obtain the amplitude of driving gear matrix steady state solution；

S3: by the elastic interlayer material chosen, the amplitude of driving gear matrix steady state solution is reduced and trend towards null value； With

S4: set up the two-freedom kinetics equation of elastic interlayer type vibration damping driven gear according to S2 step and S3 step, Choose elastic interlayer material the steady state solution of elastic interlayer type vibration damping driven gear matrix to be reduced and trend towards null value, thus according to S1 step makes the driving error of band flexible interlayer type vibration-reduction gear system reduce and trend towards null value.

It follows that will be explained in step S1.Generally, the driving error of elastic interlayer type vibration-reduction gear is with following formula table Show:

X (t)=R_ppθ₁(t)-R_pgθ₃(t) (1)

Wherein, R_ppAnd R_pgIt is respectively the driving gear in the most intermeshing a pair elastic interlayer type vibration-reduction gear and driven The pitch radius of gear, θ₁(t) and θ₃T () is respectively the angular displacement of the matrix of driving gear and driven gear.According to the present invention, The angular displacement of the matrix of driving gear and driven gear includes the angular displacement that the angular displacement at the uniform velocity changed and vibration cause, by following Formula represents:

${\mathrm{\θ}}_{1,3}\left(t\right)={\mathrm{\θ}}_{\mathrm{1,3}}^m+{\mathrm{\θ}}_{\mathrm{1,3}}^p\cos \left({\mathrm{\ω}}_{\mathrm{1,3}}t\right)---\left(2\right)$

Wherein,The angular displacement at the uniform velocity changed for elastic interlayer type vibration damping driving gear and driven gear,For bullet Property interlayer type vibration damping driving gear and driven gear due to the angular displacement that causes of vibration, ω_1,3Angular velocity and ω for vibration_1,3= 2πn_1,3/ 60, n_1,3For elastic interlayer type vibration damping driving gear and the rotating speed of the matrix of driven gear.

For a pair normal meshed gears, there is below equation:

$R_{\mathrm{pp}}{\mathrm{\θ}}_1^m=R_{\mathrm{pg}}{\mathrm{\θ}}_3^m---\left(3\right).$

Equation (3) is substituted in formula (1) and obtains gear drive error computing formula (4):

$X\left(t\right)=R_{\mathrm{pp}}{\mathrm{\θ}}_1^p\left(t\right)-R_{\mathrm{pg}}{\mathrm{\θ}}_3^p\left(t\right)---\left(4\right).$

According to one embodiment of present invention, in S2 step, kinetics equation can obtain according to dAlembert principle. Described kinetics equation can be:

$I_1{\stackrel{\·\·}{\mathrm{\θ}}}_1+k_1{\mathrm{\θ}}_1+k_2({\mathrm{\θ}}_1-{\mathrm{\θ}}_2)=T_m+T_p\sin \left({\mathrm{\ω}}_{1}t\right)---\left(5\right)$

$I_2{\stackrel{\·\·}{\mathrm{\θ}}}_2-k_2({\mathrm{\θ}}_1-{\mathrm{\θ}}_2)=T_o---\left(6\right)$

Wherein, θ₁And θ₂It is respectively angular displacement and the angular displacement of involute contour body of elastic interlayer type vibration damping driving gear； k₁Torsional rigidity for gear matrix；k₂Torsional rigidity for elastic interlayer；T_mAnd T_pIt is respectively the at the uniform velocity change of pair of engaged gears The moment of resistance that the meshing resistance square changed and vibration cause；T_oFor the meshing resistance square of gear, T_o=F_o×R_pp, wherein F_oFor engagement Power；I₁Rotary inertia for driving gear；I₂It is used to relative to the rotary inertia of gear centre, described rotation for involute contour body The value of amount is determined by formula for translation of axis (7):

I₂=mL²+I₂₀ (7)

Wherein, m is the quality of involute contour body, and L is the center of mass point o ' length to gear centre of the involute of profile body Degree, I₂₀For the involute contour body rotary inertia (as shown in Figure 3) relative to self center of mass point o '.

Formula (5) and (6) are carried out following coordinate transform, to eliminate the at the uniform velocity changing unit in formula (5) and (6):

$({\mathrm{\θ}}_1-\frac{T_m+T_o}{k_1},{\mathrm{\θ}}_2-\frac{T_m{k}_2+T_o(k_1+k_2)}{k_1{k}_2})\→({\mathrm{\θ}}_1^p,{\mathrm{\θ}}_2^p)---\left(8\right).$

Then, coordinate (8) is substituted into acquisition below equation in formula (5) and (6):

$I_1{\stackrel{\·\·}{\mathrm{\θ}}}_1^p+k_1{\mathrm{\θ}}_1^p+k_2({\mathrm{\θ}}_1^p-{\mathrm{\θ}}_2^p)=T_p\sin \left({\mathrm{\ω}}_{1}t\right)---\left(9\right)$

$I_2{\stackrel{\·\·}{\mathrm{\θ}}}_2^p-k_2({\mathrm{\θ}}_1^p-{\mathrm{\θ}}_2^p)=0---\left(10\right),$

The general solution of equation group is expressed as:

Formula (11) is substituted in formula (9) and (10) and obtains following driving gear matrix and involute contour body stable state The amplitude solved:

Wherein,KnowIt is respectively elastic interlayer type vibration damping driving gear and the amplitude of driven gear.

In S3 step, according to known involute contour body relative to the rotary inertia I of gear centre₂With elastic interlayer Formula vibration damping driving gear angular velocity of vibration ω₁Choose elastic interlayer material k₂, make the rigidity of elastic interlayer material meet such as the following Formula:

k₂=I₂ω₁ ² (14)。

Then, equation (14) is substituted into (13) acquisition below equation:

Now, elastic interlayer type vibration damping driving gear is by moment produced by elastomeric materialWith elastic interlayer type Oscillating component moment T of vibration damping driving gear matrix_pEquivalence is reversely cancelled out each other so that according to formula (12), elastic interlayer The oscillating component amplitude of formula vibration damping driving gear matrix is

Further, in step s 4, by the angular displacement of the matrix of elastic interlayer type vibration damping driven gear₃, angle of throw speed Degree ω₃Torsional rigidity k with matrix₃Replace θ₁、ω₁And k₁Substitute into formula and equation (5)-(15), the most permissible The oscillating component amplitude obtaining elastic interlayer type vibration damping driven gear matrix is

The derivation of driven gear is identical with the derivation of driving gear, will not be described in great detail at this.

When meeting formula (16) and when (17) zero, obtain the transmission of gear by mistake according to gear drive error computing formula (4) Difference is:

The method reducing gear drive error according to the present invention uses elastic interlayer type vibration-reduction gear, is had by selection The elastomeric material of certain rigidity forms elastic interlayer so that the amplitude of the oscillating component of driving gear matrix and driven gear matrix Reduce and trend towards null value, and then gear-driven error can be reduced, gear drive error can be reduced the most ideally To zero.

Although the exemplary embodiments of the present invention is illustrated, but it is clear that it will be understood by those skilled in the art that Can be changed without departing substantially from the case of spirit and principles of the present invention, its scope is in claims and its equivalent It is defined.

Claims (16)

1. an elastic interlayer type vibration-reduction gear, including:

Gear matrix, described gear matrix includes circular body and equally distributed many along the circumferencial direction of described circular body Individual gear teeth base portion；

Involute contour body, the both sides of each in the plurality of gear teeth base portion are respectively arranged with described involute contour body； With

Elastic interlayer, described elastic interlayer is arranged between described gear teeth base portion and described involute contour body in a sealing fashion, Each described gear teeth base portion is made to form gear teeth with the involute contour body of both sides and elastic interlayer.

Elastic interlayer type vibration-reduction gear the most according to claim 1, wherein, described elastic interlayer is pasted onto described gear teeth base Between portion and described involute contour body.

Elastic interlayer type vibration-reduction gear the most according to claim 2, wherein, described elastic interlayer is by acrylate AB Glue, QN-906AB glue, QN-505AB glue or KEYDAK (KD-340) anoxia glue are at described gear teeth base portion and described involute Between profile body.

Elastic interlayer type vibration-reduction gear the most according to claim 1, wherein, described elastic interlayer is welded on the described gear teeth Between base portion and described involute contour body.

Elastic interlayer type vibration-reduction gear the most according to claim 4, wherein, described welding include laser welding, argon arc welding, Any one of plasma weldering, infrared wire bonding, vacuum electric bundle weldering are welded.

Elastic interlayer type vibration-reduction gear the most according to claim 1, wherein, described elastic interlayer is made up of elastomeric material.

Elastic interlayer type vibration-reduction gear the most according to claim 6, wherein, the rigidity of described elastomeric material at 10E3～ In the range of 10E8N/m.

Elastic interlayer type vibration-reduction gear the most according to claim 6, wherein, described elastomeric material be chliorinated polyvinyl chloride, Polymer rubber alloy, aluminium alloy or copper alloy.

Elastic interlayer type vibration-reduction gear the most according to claim 1, wherein, described elastic interlayer is sized such that Width is transverse tooth thickness 0.01～0.3 times of described elastic interlayer, an a length of fully teeth height of described elastic interlayer.

10. the method reducing gear drive error, described method uses elastic interlayer type according to claim 1 to subtract Shake gear, said method comprising the steps of:

S1: derive only with the gear drive error computing formula of oscillating component；

S2: the only two-freedom kinetics equation of elastic interlayer type vibration damping driving gear with oscillating component of deriving, and obtain The amplitude of driving gear matrix steady state solution；

S3: by the elastic interlayer material chosen, the amplitude of described driving gear matrix steady state solution is reduced and trend towards null value； With

S4: set up the two-freedom kinetics side of elastic interlayer type vibration damping driven gear according to described S2 step and described S3 step Journey, chooses elastic interlayer material and the steady state solution of elastic interlayer type vibration damping driven gear matrix is reduced and trend towards null value, thus The driving error making band flexible interlayer type vibration-reduction gear system according to described S1 step reduces and trends towards null value.

11. methods according to claim 10, wherein, described S1 step farther includes:

The driving error of described elastic interlayer type vibration-reduction gear represents with following formula:

X (t)=R_ppθ₁(t)-R_pgθ₃(t) (1)

Wherein, R_ppAnd R_pgIt is respectively the driving gear in elastic interlayer type vibration-reduction gear described in intermeshing a pair and driven tooth The pitch radius of wheel, θ₁(t) and θ₃T () is respectively the angular displacement of the matrix of described driving gear and described driven gear；

The angular displacement of the matrix of described driving gear and described driven gear includes what the angular displacement at the uniform velocity changed and vibration caused Angular displacement, is represented by following formula:

${\mathrm{\θ}}_{1,3}\left(t\right)={\mathrm{\θ}}_{\mathrm{1,3}}^m+{\mathrm{\θ}}_{\mathrm{1,3}}^p\cos \left({\mathrm{\ω}}_{\mathrm{1,3}}t\right)---\left(2\right)$

Wherein,The angular displacement at the uniform velocity changed for described elastic interlayer type vibration damping driving gear and driven gear,For described The angular displacement that elastic interlayer type vibration damping driving gear and driven gear cause due to vibration, ω_1,3Angular velocity and ω for vibration_1,3 =2 π n_1,3/ 60, n_1,3For described elastic interlayer type vibration damping driving gear and the rotating speed of the matrix of driven gear；

For a pair normal meshed gears, there is below equation:

$R_{\mathrm{pp}}{\mathrm{\θ}}_1^m=R_{\mathrm{pg}}{\mathrm{\θ}}_3^m---\left(3\right);$ And

Equation (3) is substituted in formula (1) and obtains described gear drive error computing formula (4):

$X\left(t\right)=R_{\mathrm{pp}}{\mathrm{\θ}}_1^p\left(t\right)-R_{\mathrm{pg}}{\mathrm{\θ}}_3^p\left(t\right)---\left(4\right).$

12. methods according to claim 11, wherein, described S2 step farther includes:

According to the described kinetics equation that dAlembert principle acquisition is following:

$I_1{\stackrel{\·\·}{\mathrm{\θ}}}_1+k_1{\mathrm{\θ}}_1+k_2({\mathrm{\θ}}_1-{\mathrm{\θ}}_2)=T_m+T_p\sin \left({\mathrm{\ω}}_{1}t\right)---\left(5\right)$

$I_2{\stackrel{\·\·}{\mathrm{\θ}}}_2-k_2({\mathrm{\θ}}_1-{\mathrm{\θ}}_2)=T_o---\left(6\right)$

Wherein, θ₁And θ₂It is respectively the angular displacement of described elastic interlayer type vibration damping driving gear matrix and described involute contour body Angular displacement；k₁Torsional rigidity for described gear matrix；k₂Torsional rigidity for described elastic interlayer；T_mAnd T_pIt is respectively institute State the moment of resistance at the uniform velocity changed of pair of engaged gears and vibrate the moment of resistance caused；T_oFor the engagement moment of gear, T_o=F_o× R_pp, wherein F_oFor engagement force；I₁Rotary inertia for described driving gear；I₂For described involute contour body relative in gear The rotary inertia of the heart, the value of described rotary inertia is determined by formula for translation of axis (7):

I₂=mL²+I₂₀ (7)

Wherein, m is the quality of involute contour body, and L is the center of mass point o ' length to gear centre of the involute of profile body, I₂₀ For the involute contour body rotary inertia relative to self center of mass point o '.

13. methods according to claim 12, wherein:

Formula (5) and (6) are carried out following coordinate transform, to eliminate the at the uniform velocity changing unit in formula (5) and (6):

$({\mathrm{\θ}}_1-\frac{T_m+T_o}{k_1},{\mathrm{\θ}}_2-\frac{T_m{k}_2+T_o(k_1+k_2)}{k_1{k}_2})\→({\mathrm{\θ}}_1^p,{\mathrm{\θ}}_2^p)---\left(8\right);$

Coordinate (8) is substituted in formula (5) and (6) and obtains below equation:

$I_1{\stackrel{\·\·}{\mathrm{\θ}}}_1^p+k_1{\mathrm{\θ}}_1^p+k_2({\mathrm{\θ}}_1^p-{\mathrm{\θ}}_2^p)=T_p\sin \left({\mathrm{\ω}}_{1}t\right)---\left(9\right)$

$I_2{\stackrel{\·\·}{\mathrm{\θ}}}_2^p-k_2({\mathrm{\θ}}_1^p-{\mathrm{\θ}}_2^p)=0---\left(10\right),$

The general solution of equation group is expressed as:

And

Formula (11) is substituted into formula (9) and (10) and obtains following described driving gear matrix and involute contour body steady state solution Amplitude:

Wherein,WithIt is respectively described elastic interlayer type vibration damping driving gear and the amplitude of driven gear.

14. methods according to claim 13, wherein, described S3 step farther includes:

According to known described involute contour body relative to the rotary inertia I of gear centre₂With elastic interlayer type vibration damping driving tooth Wheel angular velocity of vibration ω₁Choose elastic interlayer material k₂, make the rigidity of described elastic interlayer material meet below equation:

$k_2=I_2{\mathrm{\ω}}_1^2---\left(14\right);$ And

Equation (14) is brought in formula (13), it is thus achieved that below equation:

Now, described elastic interlayer type vibration damping driving gear leads to moment produced by described elastomeric materialWith described elasticity every Oscillating component moment T of laminar vibration damping driving gear matrix_pEquivalence is reversely cancelled out each other so that according to formula (12), described The oscillating component amplitude of elastic interlayer type vibration damping driving gear matrix is

15. methods according to claim 14, wherein, in described step S4, by elasticity interlayer type vibration damping driven gear The angular displacement of matrix₃, angular velocity of vibration ω₃Torsional rigidity k with matrix₃Replace θ₁、ω₁And k₁Substitute into formula and equation (5)-(15), thus the oscillating component amplitude obtaining described elastic interlayer type vibration damping driven gear matrix is

16. methods according to claim 15, wherein, when meeting formula (16) and (17), according to described gear drive Error calculation formula (4) obtains the driving error of gear: