CN109902414A - Ultralow frequency high-damping vibration isolator and parameter determination method, device and track - Google Patents
Ultralow frequency high-damping vibration isolator and parameter determination method, device and track Download PDFInfo
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- CN109902414A CN109902414A CN201910174043.4A CN201910174043A CN109902414A CN 109902414 A CN109902414 A CN 109902414A CN 201910174043 A CN201910174043 A CN 201910174043A CN 109902414 A CN109902414 A CN 109902414A
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Abstract
In ultralow frequency high-damping vibration isolator and parameter determination method, device and track provided by the embodiments of the present application, it is related to rail traffic vibration damping field；It include: positive rigidity elastic component, negative stiffness elastic component and controllable damping part in vibration isolator, the positive stiffness coefficient of vibration isolator is determined according to the largest deformation amount of vibration isolator, and obtain the Raw performance value of negative stiffness elastic component, and then the relational expression of the stiffness coefficient of vibration isolator and the negative stiffness coefficient of negative stiffness elastic component is established, determine negative stiffness coefficient.And the relational expression of the controllable damping force of the support reaction according to suffered by vibration isolator and controllable damping part determines controllable damping force.And then vibration isolator can be made to reduce intrinsic frequency and vibration is inhibited to have good effect, and when vibration isolator is applied in rail system, can be very good to reduce the train bring hazard of vibration to orbit.
Description
Technical field
This application involves rail traffic vibration damping fields, in particular to a kind of ultralow frequency high-damping vibration isolator and parameter
Determine method, apparatus and track.
Background technique
With the development of rail traffic, more and more cities are provided with the track vehicles such as subway, light rail, facilitate
People's lives.But when train in orbit when driving, the vibration of environment will be caused, and the vibration of environment will affect passenger
Health.The vibration of environment and the structure of track are related, and steel spring floating slab track is vibration damping generally acknowledged at present in the prior art
The best track of effect, and possess wider vibration damping frequency band.But relatively due to the intrinsic frequency of steel spring floating slab track
Height, and then be easy to produce covibration, and when generating resonance, since the amplitude of vibration is big, and then also to the harm of environment
It is bigger.
Summary of the invention
The embodiment of the present application is to provide a kind of ultralow frequency high-damping vibration isolator and parameter determination method, device and track,
Its Oscillation Amplitude that can alleviate floating plate track is excessive, the unconspicuous problem of effectiveness in vibration suppression.
In a first aspect, the embodiment of the present application provides a kind of parameter determination method of vibration isolator, the vibration isolator includes: just
Rigidity elastic component, negative stiffness elastic component and controllable damping part；
Default largest deformation amount according to the vibration isolator in vertical vibration direction obtains the just rigid coefficient；
Obtain the installation in the vibration isolator of the initial length, the negative stiffness elastic component of the negative stiffness elastic component
Number and when the vertical positive rigidity elastic component of the negative stiffness elastic component, the length of the negative stiffness elastic component；
Construct the stiffness coefficient of the vibration isolator and the negative stiffness coefficient of the negative stiffness elastic component, the positive rigidity system
The first relational expression that several, the described initial length, the installation number and the length determine；Wherein, the rigidity of the vibration isolator
Coefficient value should meet the default largest deformation amount that the largest deformation amount in vertical vibration direction of the vibration isolator is less than；
The vibration isolator stiffness coefficient can minimalization in value range when, calculated according to first relational expression
The negative stiffness coefficient out.
In the application embodiment, since vibration isolator includes positive rigidity elastic component, negative stiffness elastic component and controllable resistance
Damping member, by the way that the intrinsic frequency of floating plate track can be reduced by positive rigidity elastic component and the mutual cooperation of negative stiffness elastic component, into
And vibration isolation range is improved, and determine that the coefficient of elasticity of negative stiffness elastic component can guarantee by the step in the above method
The train run on floating plate track can with while safe driving as far as possible improve vibration isolator vibration isolation range, also just quite
In improving vibration isolating effect.And due to being additionally provided with controllable damping part in vibration isolator, can inhibit to vibrate.Therefore, pass through by
The mutual cooperation of positive rigidity elastic component, negative stiffness elastic component and controllable damping part can be very good reduction floating plate track and be drawn
The vibrating effect risen.
Optionally, in the stiffness coefficient for constructing the vibration isolator and the negative stiffness coefficient, the positive stiffness coefficient, described
The first relational expression that initial length, the installation number and the length determine, comprising:
Vibration isolator power suffered by vertical vibration direction and the vibration isolator are obtained in the deformation in vertical vibration direction
The second relational expression between amount, wherein in second relational expression, vibration isolator power suffered by vertical vibration direction with
The positive stiffness coefficient of the positive rigidity elastic component and the damping force of the controllable damping part are positively correlated, and the vibration isolator is in vertical vibration
Power suffered by dynamic direction is also related to the initial length, the installation number, the length and the negative stiffness coefficient；
To the deformation quantity derivation in second relational expression, first relational expression is obtained.
The second relational expression that force analysis is determined first is carried out to vibration isolator in this application, can intuitively react floating
Whether the bearing capacity of plate track meets needs, so that passing through the calculated negative stiffness coefficient of the first relational expression more section
It learns.
Optionally, second relational expression are as follows:
Wherein, F is vibration isolator power suffered by vertical vibration direction, f0For the initial polarization power of the vibration isolator, Fd
For damping force, ZcFor the dimensionless hysteresis amount of coulomb friction, X is the distance that the positive rigidity part shortens,It is described just rigid
Spend the speed that part shortens, kvIt for the positive stiffness coefficient, is determined by the default largest deformation amount x, l is when the negative stiffness bullet
Property part perpendicular to the positive rigidity elastic component when, the length of the negative stiffness elastic component, L be the negative stiffness elastic component it is initial
Length, n are the number of the negative stiffness elastic component, are khThe negative stiffness coefficient.
In the embodiment of the present application, it can be seen that calculating vibration isolator in vertical vibration from the expression formula of the second relational expression
The initial polarization power of vibration isolator and the dimensionless hysteresis amount of coulomb friction are also contemplated when power suffered by direction, so that calculating
Vibration isolator power suffered by vertical vibration direction it is more accurate.
Optionally, second relational expression is obtained as follows:
Establish third relational expression: F=Fv+Fi；
Wherein, FvFor the positive rigidity elastic component and controllable damping part power suffered by vertical vibration direction
With FiThe component for shortening direction along the positive rigidity part is being projected to for the negative stiffness elastic component；
Establish the 4th relational expression: F=Fv+Fhsinα；
Wherein, FhFor power suffered by the negative stiffness elastic component, the α be the negative stiffness elastic component and it is described just just
The complementary angle of the acute angle of elastic component is spent,
Establish the 5th relational expression:
Second relationship is obtained according to the third relational expression, the 4th relational expression and the 5th relational expression
Formula.
It in the embodiment of the present application, can be with by the mutual iteration of third relational expression, the 4th relational expression and the 5th relational expression
The second relational expression is obtained, and then vibration isolator can be obtained when vertical vibration direction vibrates, the stress condition of each elastic component,
It is analyzed convenient for the effectiveness in vibration suppression to vibration isolator.
Optionally, after calculating the negative stiffness coefficient according to first relational expression, the method also includes:
Judge whether the negative stiffness coefficient is greater than the stiffness coefficient of the vibration isolator；
If the negative stiffness coefficient is greater than the stiffness coefficient of the vibration isolator, by the desirable of the stiffness coefficient of the vibration isolator
Value range reduces preset section from minimum, and determine the vibration isolator stiffness coefficient newly can value range；
The vibration isolator stiffness coefficient it is new can minimalization in value range when, according to first relationship
Formula calculates the negative stiffness coefficient.
When the negative stiffness coefficient obtained in the embodiment of the present application by the first relational expression, it is also necessary to judged, so that
The value of negative stiffness coefficient is reasonable, so that vibration isolator reaches better effectiveness in vibration suppression.
Optionally, first relational expression are as follows:
Wherein, kvIt for the positive stiffness coefficient, is determined by the default largest deformation amount x, l is when the negative stiffness elasticity
When part is perpendicular to the positive rigidity elastic component, the length of the negative stiffness elastic component, L is the initial length of the negative stiffness elastic component
Degree, n are the number of the negative stiffness elastic component, khFor the negative stiffness coefficient, K is the stiffness coefficient of the vibration isolator.
In the embodiment of the present application, pass through the first relational expression, it can be seen that the stiffness coefficient of vibration isolator and positive stiffness coefficient
With the relationship of negative stiffness coefficient, convenient for carrying out reasonable value in the stiffness coefficient and positive stiffness coefficient for determining vibration isolator, into
And the negative stiffness coefficient of vibration isolator can be determined faster.
Optionally, the method also includes:
It obtains suffered by the quantity of the vibration isolator below floating plate and the vibration isolator below the floating plate
Support reaction；
The controllable damping part is determined according to support reaction suffered by the quantity of the vibration isolator and the vibration isolator
Damp force parameter.
In the application embodiment, the damping force parameter of controllable damping part can be determined through the above way, is passed through
The reasonable damping force parameter of setting can inhibit to vibrate, and have better effectiveness in vibration suppression convenient for floating plate track.
Optionally, the support reaction according to suffered by the quantity of the vibration isolator, the vibration isolator and following 6th relationships
Formula determines the damping force parameter of the controllable damping part:
Wherein, Zs(xi, t) and it is displacement of the floating plate in t moment vertical vibration,For to Zs(xi, t) and displacement
Derivation indicates the floating plate in the speed of t moment vertical vibration, N is the number of the vibration isolator below the floating plate
Amount, FssjFor support reaction suffered by the vibration isolator.
Second aspect, this application provides a kind of parameter determining device of vibration isolator, the vibration isolator includes: positive rigidity bullet
Property part, negative stiffness elastic component and controllable damping part；Described device includes:
First data acquisition module is obtained for the default largest deformation amount according to the vibration isolator in vertical vibration direction
The just rigid coefficient.
Second data acquisition module, for obtaining initial length, the negative stiffness elastic component of the negative stiffness elastic component
Installation number in the vibration isolator and when the vertical positive rigidity elastic component of the negative stiffness elastic component, it is described negative
The length of rigidity elastic component.
Construct module, for construct the stiffness coefficient of the vibration isolator and the negative stiffness coefficient of the negative stiffness elastic component,
The first relational expression that the positive stiffness coefficient, the initial length, the installation number and the length determine；Wherein, described
The largest deformation amount in vertical vibration direction that the stiffness coefficient value of vibration isolator should meet the vibration isolator is less than default maximum
Deformation quantity.
Parameter determination module, for the stiffness coefficient in the vibration isolator can minimalization in value range when, according to
First relational expression calculates the negative stiffness coefficient.
The third aspect, present invention also provides a kind of ultralow frequency high-damping vibration isolators, comprising: positive rigidity elastic component is born just
Spend elastic component and controllable damping part；Wherein, the damping force of the negative stiffness coefficient of the negative stiffness elastic component and controllable damping part by
Step either in above-mentioned first aspect in method is determined.
Fourth aspect, present invention also provides a kind of tracks, including described in rail, floating plate and the above-mentioned third aspect
Ultralow frequency high-damping vibration isolator, the rail are set to above the floating plate, and are connect by fastener with the floating plate,
The ultralow frequency high-damping vibration isolator is set to below the floating plate.
5th aspect, present invention also provides a kind of readable storage medium storing program for executing, are stored thereon with computer program, the calculating
Machine program either executes in above-mentioned first aspect the step in method when being run by processor.
To enable the above objects, features, and advantages of the application to be clearer and more comprehensible, the embodiment of the present application is cited below particularly, and match
Appended attached drawing is closed, is described in detail below.
Detailed description of the invention
Technical solution in ord to more clearly illustrate embodiments of the present application, below will be to needed in the embodiment attached
Figure is briefly described, it should be understood that the following drawings illustrates only some embodiments of the application, therefore is not construed as pair
The restriction of range for those of ordinary skill in the art without creative efforts, can also be according to this
A little attached drawings obtain other relevant attached drawings.
Fig. 1 is a kind of flow diagram of vibration isolator parameter determination method provided by the embodiments of the present application；
Fig. 2 is a kind of structural schematic diagram of vibration isolator provided by the embodiments of the present application；
Fig. 3 is the structural schematic diagram of another vibration isolator provided by the embodiments of the present application；
Fig. 4 is the flow diagram of another vibration isolator parameter determination method provided by the embodiments of the present application；
Fig. 5 is the flow diagram of another vibration isolator parameter determination method provided by the embodiments of the present application；
Fig. 6 is the flow diagram of another vibration isolator parameter determination method provided by the embodiments of the present application；
Fig. 7 is the flow diagram of another vibration isolator parameter determination method provided by the embodiments of the present application；
Fig. 8 is a kind of time domain of support reaction suffered by traditional steel spring and quasi-zero stiffness vibration isolators provided by the embodiments of the present application
With the contrast schematic diagram of frequency domain；
Fig. 9 be a kind of traditional steel spring and magnetorheological damping vibration isolator support reaction provided by the embodiments of the present application time domain and
The contrast schematic diagram of frequency domain；
Figure 10 is that a kind of traditional steel spring provided by the embodiments of the present application and ultralow frequency high-damping nonlinear isolation device branch are anti-
The time domain of power and the contrast schematic diagram of frequency domain；
Figure 11 is a kind of time domain of the acceleration of traditional steel spring and quasi-zero stiffness vibration isolators provided by the embodiments of the present application
With the contrast schematic diagram of frequency domain；
Figure 12 be the acceleration of a kind of traditional steel spring and magnetorheological damping vibration isolator provided by the embodiments of the present application when
The contrast schematic diagram in domain and frequency domain；
Figure 13 is that a kind of traditional steel spring and ultralow frequency high-damping nonlinear isolation device provided by the embodiments of the present application add
The time domain of speed and the contrast schematic diagram of frequency domain；
Figure 14 is a kind of functional block diagram of vibration isolator parameter determining device provided by the embodiments of the present application.
Specific embodiment
To keep the purposes, technical schemes and advantages of the embodiment of the present application clearer, below in conjunction with the embodiment of the present application
In attached drawing, technical solutions in the embodiments of the present application is described, it is clear that described embodiment is the application a part
Embodiment, instead of all the embodiments.The component of the embodiment of the present application being usually described and illustrated herein in the accompanying drawings can be with
It arranges and designs with a variety of different configurations.
It should also be noted that similar label and letter indicate similar terms in following attached drawing, therefore, once a certain Xiang Yi
It is defined in a attached drawing, does not then need that it is further defined and explained in subsequent attached drawing.
In the description of the present application, it is also necessary to which explanation is unless specifically defined or limited otherwise, term " setting ",
" installation ", " connected ", " connection " shall be understood in a broad sense, for example, it may be fixedly connected, may be a detachable connection or one
Connect to body；It can be mechanical connection, be also possible to be electrically connected；It can be directly connected, it can also be indirect by intermediary
It is connected, can be the connection inside two elastic components.For the ordinary skill in the art, can be understood with concrete condition
The concrete meaning of above-mentioned term in this application.
Fig. 1 is please referred to, the embodiment of the present application provides a kind of flow chart of vibration isolator determination method for parameter, and vibration isolator can
To include: positive rigidity elastic component, negative stiffness elastic component and controllable damping part.
Vibration isolator in the application embodiment can be applied in floating plate track, for reducing train in floating plate
The vibration of bring floating plate track during moving on rails.The positive rigidity elastic component in vibration isolator is used in this application
Make vibration isolator that there is certain stiffness coefficient, so that vibration isolator can support enough weight, negative stiffness elastic component and just rigid
Degree elastic component can be matched with mode in parallel, can reduce the intrinsic frequency of floating plate track.And in floating plate track,
Only and when the driving frequency of floating plate track is greater thanWhen intrinsic frequency, floating plate track can just play good vibration isolation
Effect, therefore, when vibration isolation range of the intrinsic frequency equivalent to increase floating plate track for lowering floating plate track.Meanwhile by
It further include controllable damping part in the vibration isolator, the effect of controllable damping part is to lower the deformation in the vertical vibration direction of floating plate
Amount, can increase the downward amount of floating plate support stiffness, and then the vibration that floating plate track can be inhibited to cause at intrinsic frequency
It is dynamic, the vibration isolation efficiency of floating plate track is further increased with this.It is described in detail below in conjunction with specific embodiment, it is listed below
For embodiment in, be with vibration isolator applied to floating plate track illustrate.The structure of vibration isolator in order to facilitate understanding, this
Application embodiment provides a kind of structural schematic diagram of vibration isolator, as shown in Figure 2.Vibration isolator is placed in floating plate track
Structural schematic diagram is as shown in Figure 3.
It can be seen that positive rigidity elastic component and negative stiffness elastic component are steel spring in Fig. 2, and negative stiffness elastic component exists
There are two in Fig. 2, it is symmetrically arranged in the two sides of positive rigidity elastic component.In fig. 3 it can be seen that vibration isolator is placed on pedestal
On, that is, the pedestal of floating plate track, and can be seen that and have multiple identical vibration isolators below a floating plate, and is more
A vibration isolator is according to certain spacing arrangement.Be provided with rail fastening above floating plate, one end of rail fastening with it is floating
Plate connection, the other end of rail fastening are connect with track.It should be noted that Fig. 2 and Fig. 3 are merely for convenience of understanding the application
Vibration isolator that embodiment provides and the schematic diagram that provides, do not play restriction effect to the vibration isolator in the embodiment of the present application.
Step S110: the default largest deformation amount according to vibration isolator in vertical vibration direction obtains just rigid coefficient.
Since the train weight travelled on floating plate track is larger, in order to guarantee the safety of train normally travel
Property；The overall structure of floating plate track should have certain rigidity, avoid during train driving since track is partially soft and
Initiation accident.And the default largest deformation amount in vertical vibration direction of floating plate track can be pressed according in actual application
It is determined according to actual demand, it can be deduced that default largest deformation amount of the vibration isolator in vertical vibration direction is 3mm.And then it determines
The positive stiffness coefficient of positive rigidity elastic component out.
Step S120: the initial length that obtains the negative stiffness elastic component, the negative stiffness elastic component are in the vibration isolator
In installation number and when the vertical positive rigidity elastic component of the negative stiffness elastic component, the negative stiffness elastic component
Length.
Since in vibration isolator provided by the embodiments of the present application, negative stiffness elastic component and positive rigidity elastic component be can be side by side
It is arranged.And vibration isolator is mounted on the lower section of floating plate, and the installation space below floating plate is limited.Therefore, it is being embodied
In mode, the initial length and negative stiffness bullet of negative stiffness elastic component can be determined according to the size in the space below floating plate
The number of property part.When default largest deformation amount of the vibration isolator in vertical vibration direction, at this time negative stiffness elastic component can with just
Rigidity elastic component is vertical, can determine the installation site of negative stiffness elastic component at this time, and then also just obtains negative stiffness elasticity
Part vertically positive rigidity elastic component when, the length of negative stiffness elastic component at this time.
Step S130: the stiffness coefficient of the vibration isolator and negative stiffness coefficient, the positive stiffness coefficient, described is constructed
The first relational expression that initial length, the installation number and the length determine；Wherein, the stiffness coefficient value of the vibration isolator
The default largest deformation amount that the largest deformation amount in vertical vibration direction of the vibration isolator is less than should be met.
First relational expression is the relational expression of the stiffness coefficient of vibration isolator Yu the negative stiffness coefficient of negative stiffness elastic component, due to just
Positive stiffness coefficient, the negative stiffness coefficient of negative stiffness elastic component, the initial length of negative stiffness elastic component, the negative stiffness of rigidity elastic component
The installation number and negative stiffness elastic component of elastic component vertically positive rigidity elastic component when negative stiffness elastic component length in above-mentioned step
It is got in rapid, so the unknown number in the first relational expression is the stiffness coefficient of vibration isolator and the negative stiffness of negative stiffness elastic component
Coefficient.
The first relational expression in the embodiment of the present application can be with are as follows:
Wherein, kvIt for the positive stiffness coefficient, is determined by the default largest deformation amount x, l is when the negative stiffness elasticity
When part is perpendicular to the positive rigidity elastic component, the length of the negative stiffness elastic component, L is the initial length of the negative stiffness elastic component
Degree, n are the number of the negative stiffness elastic component, khFor the negative stiffness coefficient, K is the stiffness coefficient of the vibration isolator.
Step S140: the vibration isolator stiffness coefficient can minimalization in value range when, according to described first
Relational expression calculates the negative stiffness coefficient.
When vibration isolator is applied to floating plate track, the stiffness coefficient of vibration isolator should meet the traffic safety driving of train
Demand, so can determine vibration isolator stiffness coefficient can value range, in vibration isolator stiffness coefficient can value range
Interior, when stiffness coefficient is smaller, the intrinsic frequency of floating plate track is lower at this time, and effectiveness in vibration suppression at this time is also better.Therefore,
When determining the value of negative stiffness coefficient, minimalization can determine to bear in value range in the stiffness coefficient of vibration isolator
The value of stiffness coefficient.For example, the stiffness coefficient of vibration isolator can value range be 9.00KN/mm-15.00KN/mm when, at this time may be used
Using take 9.00KN/mm as vibration isolator stiffness coefficient by the first relational expression determine negative stiffness elastic component in vibration isolator it is negative just
Spend coefficient.
In the embodiment of the present application, vibration isolator mutually ties positive rigidity elastic component, negative stiffness elastic component and controllable damping part
It closes, intrinsic frequency is reduced by the cooperation of positive rigidity elastic component and negative stiffness elastic component, and vibration is inhibited by controllable damping part,
And then it can achieve good effectiveness in vibration suppression.And the overall stiffness coefficient by establishing vibration isolator and negative stiffness elastic component it is negative just
First relational expression of degree coefficient determines negative stiffness coefficient, can reduce as far as possible while guaranteeing safe train operation
Vibration caused by train operation.
Optionally, referring to Fig. 4, step S130 the stiffness coefficient and the negative stiffness coefficient for constructing the vibration isolator,
The first relational expression that the positive stiffness coefficient, the initial length, the installation number and the length determine, comprising:
Step S132: vibration isolator power suffered by vertical vibration direction and the vibration isolator are obtained in vertical vibration side
To deformation quantity between the second relational expression, wherein in second relational expression, the vibration isolator is in vertical vibration direction institute
The positive stiffness coefficient of the power and the positive rigidity elastic component received and the damping force of the controllable damping part are positively correlated, the vibration isolator
The power suffered by vertical vibration direction also with the initial length, the installation number, the length and the negative stiffness coefficient
It is related；
Step S134: to the deformation quantity derivation in second relational expression, first relational expression is obtained.
That is, need to obtain is between power suffered by vibration isolator and the deformation quantity of vibration isolator in the second relational expression
Relationship.When obtaining the relationship suffered by vibration isolator between power and the deformation quantity of vibration isolator, force analysis is carried out to vibration isolator,
One end using negative stiffness elastic component far from positive rigidity elastic component as coordinate origin, with vertical positive rigidity elastic component and pass through coordinate
The straight line of origin establishes reference axis, and using vertical vibration direction as positive direction.At this point, the bearing distribution of negative stiffness elastic component is arrived
In positive direction, the relational expression between the deformation quantity of total power and vibration isolator of the vibration isolator suffered by positive direction, that is, second are established
Relational expression.When establishing the second relational expression, it is also necessary to consider the initial biasing force of vibration isolator, vibration isolator Coulomb friction power it is immeasurable
Guiding principle hysteresis amount.
In the embodiment of the present application, initial biasing force and dimensionless hysteresis amount are unrelated with the deformation quantity of vibration isolator, therefore,
After the deformation quantity derivation in the second relational expression, the first relational expression is the stiffness coefficient of vibration isolator and positive stiffness coefficient, bears just
Spend coefficient, the initial length of negative stiffness elastic component, the installation number of negative stiffness elastic component and negative stiffness elastic component vertically positive rigidity
When elastic component, the length of negative stiffness elastic component at this time, relational expression.
In the embodiment of the present application, the second relational expression are as follows:
Wherein, F is vibration isolator power suffered by vertical vibration direction, f0For the initial polarization power of the vibration isolator, Fd
For damping force, ZcFor the dimensionless hysteresis amount of coulomb friction, X is the distance that the positive rigidity part shortens,It is described just rigid
Spend the speed that part shortens, kvIt for the positive stiffness coefficient, is determined by the default largest deformation amount x, l is when the negative stiffness bullet
Property part perpendicular to the positive rigidity elastic component when, the length of the negative stiffness elastic component, L be the negative stiffness elastic component it is initial
Length, n are the number of the negative stiffness elastic component, are khThe negative stiffness coefficient.
Optionally, referring to Fig. 5, passing through available second relational expression of following steps.
Step S1322: third relational expression: F=F is establishedv+Fi；
Wherein, FvFor the positive rigidity elastic component and controllable damping part power suffered by vertical vibration direction
With FiThe component for shortening direction along the positive rigidity part is being projected to for the negative stiffness elastic component.
Step S1324: the 4th relational expression: F=F is establishedv+Fhsinα；
Wherein, wherein FhFor power suffered by the negative stiffness elastic component, the α is the negative stiffness elastic component and institute
The complementary angle of the acute angle of positive rigidity elastic component is stated,
Step S1326: the 5th relational expression is established:
Step S1328: according to the acquisition of the third relational expression, the 4th relational expression and the 5th relational expression
Second relational expression.
Certainly, step S1322, step S1324 and step S1328 can the sequence between can be replaced, executing
When this method, step S1324 can be first carried out, step S1322 is being executed, is finally executing step S1328, or first carry out step
S1328 is executing step S1324, is finally executing step S1322.
After getting the second relational expression, to the deformation quantity derivation in the second relational expression, the first relational expression can be obtained.
Referring to Fig. 6, in the embodiment of the present application, after obtaining the first relational expression through the above way, the method is also
Include:
Step S150: judge whether the negative stiffness coefficient is greater than the stiffness coefficient of vibration isolator.
Step S160: if negative stiffness coefficient be greater than vibration isolator stiffness coefficient, by the stiffness coefficient of the vibration isolator can
Value range reduces preset section from minimum, and determines that the new of stiffness coefficient of the vibration isolator can value model
It encloses.
Step S170: the vibration isolator stiffness coefficient it is new can minimalization in value range when, according to institute
It states the first relational expression and calculates the negative stiffness coefficient.
After determining negative stiffness coefficient by the first relational expression, to judge whether negative stiffness coefficient meets regulation；Example
Such as, when calculate negative stiffness coefficient be greater than vibration isolator stiffness coefficient, hence it is evident that it is against regulation.That is to say, the bright institute of vibration isolator at this time
The stiffness coefficient of the vibration isolator taken has been less than the positive stiffness coefficient of vibration isolator from far away, and then it is unknown to may cause effectiveness in vibration suppression
It is aobvious.It needs the stiffness coefficient of vibration isolator increasing preset section at this time, and determines negative stiffness again by the first relational expression
The negative stiffness coefficient of elastic element.Until the negative stiffness coefficient meet demand of negative stiffness elastic element.In other words,
In the embodiment of the present application, by the way that in the desirable range of the stiffness coefficient in vibration isolator, continuous value is to determine when negative rigid
Spend coefficient.In a specific embodiment, it when negative stiffness coefficient directly can also be determined as 0, brings the first relational expression into and calculates
The stiffness coefficient of one vibration isolator.Calculated stiffness coefficient can be used as the maximum of the stiffness coefficient of vibration isolator at this time, into
And it directly can be sequentially reduced preset section from maximum, until when reaching the effectiveness in vibration suppression of vibration isolator preferably.
What needs to be explained here is that the stiffness coefficient of theoretically vibration isolator is smaller, effectiveness in vibration suppression is better；But in reality
In the application on border, need to consider the model and parameter and negative stiffness elastic component and positive rigidity elastic component of positive rigidity elastic component
Cooperation.Therefore in actual application process, when determining the stiffness coefficient of vibration isolator, it can use MATLAB simulation software
Simulate the effectiveness in vibration suppression of vibration isolator at this time, and again by the stiffness coefficient of vibration isolator can value range change preset area
Between, the effectiveness in vibration suppression for simulating vibration isolator again is gone on this, until vibration isolator when seeking effectiveness in vibration suppression preferably
Corresponding stiffness coefficient, and negative stiffness coefficient corresponding to the stiffness coefficient.It is to illustrate with continuous 10 stiffness coefficients
Stiffness coefficient corresponding to bright vibration isolator when how to obtain effectiveness in vibration suppression preferably, and successively by number be the first stiffness coefficient,
The 9th stiffness coefficient of second stiffness coefficient ... and the tenth stiffness coefficient；In this continuous 10 stiffness coefficient, if the first rigidity
Coefficient to the 6th corresponding effectiveness in vibration suppression of stiffness coefficient successively increases, and the 6th stiffness coefficient is respectively right to the tenth stiffness coefficient
The effectiveness in vibration suppression answered successively is reduced, therefore rigid corresponding to vibration isolator when the 6th stiffness coefficient can be used as effectiveness in vibration suppression preferably
Spend coefficient.If such as the first stiffness coefficient is corresponding to the 5th stiffness coefficient there are two the identical stiffness coefficient of effectiveness in vibration suppression
Effectiveness in vibration suppression successively increases, and the 6th stiffness coefficient to the tenth corresponding effectiveness in vibration suppression of stiffness coefficient is successively reduced, and the 5th
Stiffness coefficient and the corresponding effectiveness in vibration suppression of the 6th stiffness coefficient are identical；It at this time can be by five stiffness coefficients or the 6th stiffness coefficient
Stiffness coefficient corresponding to vibration isolator when as effectiveness in vibration suppression preferably.It can also be with the 5th stiffness coefficient and the 6th stiffness coefficient weight
New section is newly set up, and successively increases the stiffness coefficient of vibration isolator according to new section.
For example, being successively spaced identical section in the 5th stiffness coefficient to six stiffness coefficients and being provided with the 51st
Stiffness coefficient, the 58th stiffness coefficient of the 52nd stiffness coefficient ..., the 59th stiffness coefficient, and again according to above-mentioned
Stiffness coefficient corresponding to vibration isolator when method determines effectiveness in vibration suppression preferably, is no longer repeated one by one herein.
It should be noted that preset section in the embodiment of the present application can be chosen according to actual needs, and
Without limiting；For example, preset section can be 0.01KN/mm；At this point, if the stiffness coefficient of vibration isolator takes 9.00KN/mm
When the negative stiffness coefficient calculated is unsatisfactory for, the stiffness coefficient of vibration isolator is being taken as 9.01KN/mm at this time, is being counted again
It calculates, until calculated negative stiffness coefficient meets needs.
Referring to Fig. 7, in the embodiment of the present application, it, can be under if vibration isolator is applied in floating plate track
The method of stating determines the damping force parameter of controllable damping force:
Step S210: the quantity for obtaining the vibration isolator below floating plate and the vibration isolation below the floating plate
Support reaction suffered by device.
What is installed below floating plate is vibration isolator, according to the size in the space below each floating plate and determines energy
The quantity of the vibration isolator of installation.Certain power is added above floating plate, and then can determine that branch suffered by each vibration isolator is anti-
Power.The power added above floating plate can be the maximum power that single floating plate can bear, by running on floating plate track
Train the biggest quality determine.And it is very nearly the same to be arranged in power suffered by multiple vibration isolators below the same floating plate, because
This can approximation regard as it is identical.And then it can be by determining that the power above floating plate determines branch suffered by each vibration isolator
Counter-force size.
Step S220: it is determined according to support reaction suffered by the quantity of the vibration isolator and the vibration isolator described controllable
The damping force parameter of damping piece.
In the application embodiment, the damping force parameter of support reaction suffered by vibration isolator and controllable damping part is positively correlated.
After the power applied on floating plate determines, then each vibration isolator can be determined according to the quantity of the vibration isolator below floating plate
Suffered support reaction, and then also determined that the damping force parameter of controllable damping part.
When obtaining the damping force parameter of controllable damping part, need to combine third formula:
Wherein, Zs(xi, t) and it is displacement of the floating plate in t moment vertical vibration,For to Zs(xi, t) and displacement
Derivation indicates the floating plate in the speed of t moment vertical vibration, N is the number of the vibration isolator below the floating plate
Amount, FssjFor support reaction suffered by the vibration isolator.
As can be seen that unknown quantity only has F from third formulad；And FdValue it is bigger, the inhibitory effect of vibration is got over
It is good.But work as FdValue it is excessive when, can will amplify high-frequency vibration；Therefore, F is being determineddValue when, can determine one
FdMaximum value, and be sequentially reduced Fd, optimal F is determined with thisd。
Determining FdMaximum value when, can according to the damping force parameter in existing magnetic rheological isolator be maximum resistance
Buddhist nun's force parameter, because negative stiffness elastic component is not added in magnetic rheological isolator, in the application embodiment
Damping force parameter is less than the damping force parameter in magnetic rheological isolator.It in turn, can be by the damping force in magnetic rheological isolator
Parameter is set as the maximum damping force parameter of the application.Then force parameter is successively damped, damping force parameter is finally determined.When
So, the amplitude reduced every time can be determines according to actual conditions.
It should be noted that when determining the damping force parameter in magnetic rheological isolator, it may be that the vibration isolation with the application
Device is in the damping force parameter under identical environment.For example, being applied in floating plate track, and the magnetic below each floating plate
The quantity for flowing vibration isolator is identical as the quantity of the vibration isolator of the application, and the positive stiffness coefficient in positive rigidity elastic component is identical.
In the embodiment of the present application, in parameter (the positive stiffness coefficient, negative stiffness system for determining vibration isolator by the above method
Several and controllable damping force parameter) during, when judging the effectiveness in vibration suppression of vibration isolator, the branch that can be on floating plate of monitoring
The acceleration of counter-force and floating plate.It can be according to being support reaction on floating plate and floating namely in the application embodiment
The acceleration of plate judges the effectiveness in vibration suppression of floating plate track, and then in presently filed embodiment, by by different parameters
After setting, the support reaction and floating plate on the available floating plate of dynamics simulation are carried out by MATLAB simulation software
Acceleration, and then judge the effectiveness in vibration suppression of floating plate track.
Show effect brought by the application below in conjunction with specific embodiment:
Be used to be analyzed in floating plate track system with several common vibration isolators, and enumerate it is several commonly every
The key parameter of vibration device, as shown in table 1.In the present embodiment, using 80km/h speed and 5 grades of the U.S. wavelength 0.1m-30m height
The operation condition of low irregularity spectrum.
Table 1
In present embodiment, floating plate track size can be 25m × 3.2m × 0.3m, and density can be 2500kg/m3,
And taking the stiffness coefficient of positive rigidity elastic component in floating plate track is 10kN/mm.According to installation of the vibration isolator below floating plate
Space gauge 450mm × 450mm (long × wide), using 2 Negative stiffness spring elastic components, taking horizontal length l is 200mm, and is born
It is 0.01 that length L, which is taken as sin α under 300mm, negative stiffness elastic component initial mounting state, under rigidity elastic component free state.It is selected
The stiffness coefficient of the application vibration isolator is 5kN/mm, and the rigidity of negative stiffness elastic element can be calculated according to the first relational expression
Coefficient is 5kN/mm.Also, go out the damping parameter F of damping piece by six relational expressions, that is, tentatively calculatingdFor 0.8kN.Meanwhile this Shen
Each parameter that please be taken in vibration isolator, which can satisfy, makes the maximum displacement of floating plate track be no more than 3mm, therefore meets vehicle
Safe driving requirement.
Below with reference to from time domain angle and frequency domain angle analyzed, in the embodiment of the present application, the vibration isolation of the application
Device can with " ultralow frequency high-damping nonlinear isolation device " name, in following narration, with " ultralow frequency high-damping it is non-linear every
Shake device " replace vibration isolator provided herein.
Traditional steel spring and quasi-zero stiffness vibration isolators are compared respectively, as shown in Figure 8；Compare traditional steel spring and magnetic current variable resistance
Buddhist nun's vibration isolator, as shown in Figure 9；Traditional steel spring and ultralow frequency high-damping nonlinear isolation device are compared, as shown in Figure 10.
In conjunction with Fig. 8, Fig. 9 and Figure 10, from time domain angle it can be seen that the support reaction maximum value of traditional steel spring vibration isolator is
26.18kN；The support reaction maximum value of magnetorheological damping vibration isolator is 25.00kN；The support reaction maximum value of quasi-zero stiffness vibration isolators
For 19.78kN, the support reaction maximum value of ultralow frequency high-damping nonlinear isolation device is 19.02kN.Thus, it will be seen that using
When ultralow frequency high-damping vibration isolator, the support reaction under floating plate is minimum, reduces 27.35% compared to steel spring floating slab track.
It should be noted that due in embodiment provided by the present application, by each vibration isolator below floating plate by
To support reaction be added the support reaction of floating plate can be obtained, and when comparing experiment, vibration isolator below floating plate
Quantity is identical, therefore can directly compare the support reaction of vibration isolator.
It is can be found that from frequency domain angle analysis: (the floating plate in floating plate track at 10Hz of traditional steel spring vibration isolator
Fundamental frequency), support reaction amplitude be 1.55kN.After magnetorheological damping vibration isolator, near intrinsic frequency 10Hz, support reaction width
Value is reduced to 0.57kN, reduces 63.22%.After quasi-zero stiffness vibration isolators, floating plate intrinsic frequency is reduced to 6.3Hz attached
Closely, support reaction amplitude is 0.61kN, reduces 60.65%.
It further, is 5Hz in one third octave center frequency after using ultralow frequency high-damping nonlinear isolation device
Place, support reaction amplitude is only 0.32kN, reduces 79.35%.
Below ultralow frequency high-damping nonlinear isolation device bring vibration damping effect will be further analyzed from the acceleration of floating plate
Fruit:
Also it is analyzed from the angle of time domain and frequency domain angle, compares traditional steel spring and quasi-zero stiffness vibration isolators respectively,
As shown in figure 11, traditional steel spring and magnetorheological damping vibration isolator are compared, as shown in figure 12, compares traditional steel spring and ultralow frequency
High-damping nonlinear isolation device, as shown in figure 13.
In conjunction with Figure 11, Figure 12 and Figure 13；In conjunction with time domain angle it can be seen that traditional steel spring floating slab track vertical vibration
Acceleration maximum value 12.25m/s2；Magnetorheological damping vibration isolator floating plate track Vertical Acceleration maximum value 11.37m/s2,
Only reduce 7.18%；Quasi-zero stiffness vibration isolators floating plate track Vertical Acceleration maximum value 11.15m/s2, only reduce
8.98%；Ultralow frequency high-damping nonlinear isolation device floating plate track Vertical Acceleration maximum value is only 4.88m/s2, drop
Low about 60.16%.
From frequency domain angle analysis it can be seen that traditional steel spring floating slab track Vertical Acceleration vibration level is in intrinsic frequency
Rate 10Hz is nearby about 115.55dB.Compared to steel spring floating slab track, hung down using magnetorheological damping vibration isolator floating plate track
It is 106.64dB at 10Hz to vibration acceleration vibration level, reduces 8.91dB；Using quasi-zero stiffness vibration isolators, floating plate is intrinsic
Frequency is reduced near 6.3Hz, and Vertical Acceleration vibration level is 106.41dB, reduces 9.14dB；Using ultralow frequency
High-damping nonlinear isolation device, floating plate track intrinsic frequency is not only reduced to 6.3Hz, but also Vertical Acceleration is reduced to
94.95dB reduces about 22.6dB than the Vertical Acceleration at steel spring floating slab track fundamental frequency.
Therefore, it can significantly find out, compare other three kinds of common vibration isolators, ultralow frequency high-damping vibration isolator is on the one hand
The transmitting of the support reaction in floating plate track is effectively inhibited, on the other hand, due to reducing the intrinsic frequency of floating plate track
Rate also just improves floating plate support reaction low frequency vibration isolation frequency range.It can be good at inhibiting vibration.
Please refer to Figure 14, present invention also provides a kind of structural block diagram of the parameter determining device 10 of vibration isolator, it is described every
The device that shakes includes: positive rigidity elastic component, negative stiffness elastic component and controllable damping part；Described device 10 includes:
First data acquisition module 110, for the default largest deformation amount according to the vibration isolator in vertical vibration direction
Obtain the just rigid coefficient.
Second data acquisition module 120, for obtaining initial length, the negative stiffness elasticity of the negative stiffness elastic component
Installation number of the part in the vibration isolator and when the vertical positive rigidity elastic component of the negative stiffness elastic component, it is described
The length of negative stiffness elastic component.
Module 130 is constructed, for constructing the stiffness coefficient and the negative stiffness coefficient, the positive rigidity system of the vibration isolator
The first relational expression that several, the described initial length, the installation number and the length determine；Wherein, the rigidity of the vibration isolator
The largest deformation amount in vertical vibration direction that coefficient value should meet the vibration isolator is less than default largest deformation amount.
Parameter determination module 140, for the stiffness coefficient in the vibration isolator can minimalization in value range when, root
The negative stiffness coefficient is calculated according to first relational expression.
Optionally, parameter determination module 140 includes:
Second relational expression determining module, for obtaining vibration isolator power suffered by vertical vibration direction and the vibration isolation
Second relational expression of the device between the deformation quantity in vertical vibration direction, wherein in second relational expression, the vibration isolator exists
The damping force of the positive stiffness coefficient and the controllable damping part of power suffered by vertical vibration direction and the positive rigidity elastic component is just
Correlation, vibration isolator power suffered by vertical vibration direction also with the initial length, the installation number, the length and
The negative stiffness coefficient is related；
First relational expression determining module, for the deformation quantity derivation in second relational expression, obtaining described the
One relational expression.
Optionally, second relational expression are as follows:
Wherein, F is vibration isolator power suffered by vertical vibration direction, f0For the initial polarization power of the vibration isolator, Fd
For damping force, ZcFor the dimensionless hysteresis amount of coulomb friction, X is the distance that the positive rigidity part shortens,It is described just rigid
Spend the speed that part shortens, kvIt for the positive stiffness coefficient, is determined by the default largest deformation amount x, l is when the negative stiffness bullet
Property part perpendicular to the positive rigidity elastic component when, the length of the negative stiffness elastic component, L be the negative stiffness elastic component it is initial
Length, n are the number of the negative stiffness elastic component, are khThe negative stiffness coefficient.
Optionally, the second relational expression determining module includes:
First establishes module, for establishing third relational expression: F=Fv+Fi；
Wherein, FvFor the positive rigidity elastic component and controllable damping part power suffered by vertical vibration direction
With FiThe component for shortening direction along the positive rigidity part is being projected to for the negative stiffness elastic component；
Second establishes module, for establishing the 4th relational expression: F=Fv+Fhsinα；
Wherein, FhFor power suffered by the negative stiffness elastic component, the α be the negative stiffness elastic component and it is described just just
The complementary angle of the acute angle of elastic component is spent,
Third establishes module, for establishing the 5th relational expression:
First determining module, for according to the third relational expression, the 4th relational expression and the 5th relational expression
Obtain second relational expression.
Optionally, after calculating the negative stiffness coefficient according to first relational expression, described device further include:
Judgment module, for judging whether the negative stiffness coefficient is greater than the stiffness coefficient of vibration isolator.
Second determining module, when for being greater than the stiffness coefficient of vibration isolator in negative stiffness coefficient, by the rigid of the vibration isolator
Degree coefficient can value range reduces preset section from minimum, and determine the vibration isolator stiffness coefficient newly
It can value range；
Computing module, for the stiffness coefficient in the vibration isolator it is new can minimalization in value range when, root
The negative stiffness coefficient is calculated according to first relational expression.
Optionally, first relational expression are as follows:
Wherein, kvIt for the positive stiffness coefficient, is determined by the default largest deformation amount x, l is when the negative stiffness elasticity
When part is perpendicular to the positive rigidity elastic component, the length of the negative stiffness elastic component, L is the initial length of the negative stiffness elastic component
Degree, n are the number of the negative stiffness elastic component, khFor the negative stiffness coefficient, K is the stiffness coefficient of the vibration isolator.
Optionally, described device further include:
Obtain module, below the quantity and the floating plate for obtaining the vibration isolator below floating plate described in
Support reaction suffered by vibration isolator；
Third determining module is determined for the support reaction according to suffered by the quantity of the vibration isolator and the vibration isolator
The damping force parameter of the controllable damping part.
Optionally, the support reaction according to suffered by the quantity of the vibration isolator, the vibration isolator and following 6th relationships
Formula determines the damping force parameter of the controllable damping part:
Wherein, Zs(xi, t) and it is displacement of the floating plate in t moment vertical vibration,For to Zs(xi, t) and displacement
Derivation indicates the floating plate in the speed of t moment vertical vibration, N is the number of the vibration isolator below the floating plate
Amount, FssjFor support reaction suffered by the vibration isolator.
Present invention also provides a kind of ultralow frequency high-damping vibration isolators, comprising: positive rigidity elastic component, negative stiffness elastic component and
Controllable damping part；Wherein, the negative stiffness coefficient of the negative stiffness elastic component and the damping force of controllable damping part are by above-mentioned method
It determines.
Present invention also provides a kind of tracks, including rail, floating plate and above-mentioned ultralow frequency high-damping vibration isolator, institute
It states rail to be set to above the floating plate, and is connect by fastener with the floating plate, the ultralow frequency high-damping vibration isolation
Device is set to below the floating plate.
Present invention also provides a kind of readable storage medium storing program for executing, are stored thereon with computer program, the computer program quilt
The step in method is as above stated in operation when processor executes.
Ultralow frequency high-damping vibration isolator and parameter determination method, device and the track provided in the application embodiment
In, positive rigidity elastic component, negative stiffness elastic component and controllable damping part are be combined with each other in vibration isolator, and true using the above method
Respective parameter is made, so that vibration isolator is reducing intrinsic frequency and vibration is inhibited to have good expression effect.And work as vibration isolation
When device is applied in rail system, it can be very good to reduce the train bring hazard of vibration to orbit.
In embodiment provided herein, it should be understood that disclosed device and method, it can also be by other
Mode realize.The apparatus embodiments described above are merely exemplary, for example, the flow chart and block diagram in attached drawing are shown
According to device, the architectural framework in the cards of method and computer program product, function of multiple embodiments of the application
And operation.In this regard, each box in flowchart or block diagram can represent one of a module, section or code
Point, a part of the module, section or code includes one or more for implementing the specified logical function executable
Instruction.It should also be noted that function marked in the box can also be attached to be different from some implementations as replacement
The sequence marked in figure occurs.For example, two continuous boxes can actually be basically executed in parallel, they sometimes may be used
To execute in the opposite order, this depends on the function involved.It is also noted that each of block diagram and or flow chart
The combination of box in box and block diagram and or flow chart can be based on the defined function of execution or the dedicated of movement
The system of hardware is realized, or can be realized using a combination of dedicated hardware and computer instructions.
In addition, each functional module in each embodiment of the application can integrate one independent portion of formation together
Point, it is also possible to modules individualism, an independent part can also be integrated to form with two or more modules.
It, can be with if the function is realized and when sold or used as an independent product in the form of software function module
It is stored in a computer readable storage medium.Based on this understanding, the technical solution of the application is substantially in other words
The part of the part that contributes to existing technology or the technical solution can be embodied in the form of software products, the meter
Calculation machine software product is stored in a storage medium, including some instructions are used so that a computer equipment (can be a
People's computer, laptop, server or network equipment etc.) execute each embodiment the method for the application whole
Or part steps.And storage medium above-mentioned includes: USB flash disk, mobile hard disk, read-only memory (ROM, Read-Only
Memory), random access memory (RAM, Random Access Memory), magnetic or disk etc. are various can store journey
The medium of sequence code.It should be noted that, in this document, relational terms such as first and second and the like are used merely to one
A entity or operation with another entity or operate distinguish, without necessarily requiring or implying these entities or operation it
Between there are any actual relationship or orders.Moreover, the terms "include", "comprise" or its any other variant are intended to
Cover non-exclusive inclusion, so that the process, method, article or equipment for including a series of elements not only includes those
Element, but also including other elements that are not explicitly listed, or further include for this process, method, article or setting
Standby intrinsic element.In the absence of more restrictions, the element limited by sentence "including a ...", it is not excluded that
There is also other identical elements in the process, method, article or apparatus that includes the element.
The foregoing is merely preferred embodiment of the present application, are not intended to limit this application, for the skill of this field
For art personnel, various changes and changes are possible in this application.Within the spirit and principles of this application, made any to repair
Change, equivalent replacement, improvement etc., should be included within the scope of protection of this application.
Claims (10)
1. a kind of parameter determination method of vibration isolator, which is characterized in that the vibration isolator includes: positive rigidity elastic component, negative stiffness
Elastic component and controllable damping part；
Default largest deformation amount according to the vibration isolator in vertical vibration direction obtains the just rigid system of the positive rigidity elastic component
Number；
Obtain installation number in the vibration isolator of the initial length, the negative stiffness elastic component of the negative stiffness elastic component,
And when the vertical positive rigidity elastic component of the negative stiffness elastic component, the length of the negative stiffness elastic component；
Construct the stiffness coefficient of the vibration isolator and the negative stiffness coefficient of the negative stiffness elastic component, the positive stiffness coefficient, institute
State the first relational expression that initial length, the installation number and the length determine；Wherein, the stiffness coefficient of the vibration isolator takes
Value should meet the default largest deformation amount that the largest deformation amount in vertical vibration direction of the vibration isolator is less than；
The vibration isolator stiffness coefficient can minimalization in value range when, institute is calculated according to first relational expression
State negative stiffness coefficient.
2. the method according to claim 1, wherein being born just in the stiffness coefficient for constructing the vibration isolator with described
Spend the first relational expression that coefficient, the positive stiffness coefficient, the initial length, the installation number and the length determine, packet
It includes:
Obtain vibration isolator power suffered by vertical vibration direction and the vibration isolator vertical vibration direction deformation quantity it
Between the second relational expression, wherein in second relational expression, vibration isolator power suffered by vertical vibration direction with it is described
The positive stiffness coefficient of positive rigidity elastic component and the damping force of the controllable damping part are positively correlated, and the vibration isolator is in vertical vibration side
It is also related to the initial length, the installation number, the length and the negative stiffness coefficient to suffered power；
To the deformation quantity derivation in second relational expression, first relational expression is obtained.
3. according to the method described in claim 2, it is characterized in that, second relational expression are as follows:
Wherein, F is vibration isolator power suffered by vertical vibration direction, f0For the initial polarization power of the vibration isolator, FdFor resistance
Buddhist nun's power, ZcFor the dimensionless hysteresis amount of coulomb friction, X is the distance that the positive rigidity part shortens,For the positive rigidity part
The speed of shortening, kvIt for the positive stiffness coefficient, is determined by the default largest deformation amount x, l is when the negative stiffness elastic component
When perpendicular to the positive rigidity elastic component, the length of the negative stiffness elastic component, L is the initial length of the negative stiffness elastic component
Degree, n are the number of the negative stiffness elastic component, are khThe negative stiffness coefficient.
4. according to the method described in claim 3, it is characterized in that, obtaining second relational expression as follows:
Establish third relational expression: F=Fv+Fi；
Wherein, FvFor the positive rigidity elastic component and the sum of controllable damping part power suffered by vertical vibration direction, FiFor
The negative stiffness elastic component shortens the component in direction projecting to along the positive rigidity elastic component；
Establish the 4th relational expression: F=Fv+Fhsinα；
Wherein, FhFor power suffered by the negative stiffness elastic component, the α is the negative stiffness elastic component and the positive rigidity bullet
The complementary angle of the acute angle of property part,
Establish the 5th relational expression:
Second relational expression is obtained according to the third relational expression, the 4th relational expression and the 5th relational expression.
5. according to the method described in claim 3, it is characterized in that, calculating the negative stiffness according to first relational expression
After coefficient, the method also includes:
Judge whether the negative stiffness coefficient is greater than the stiffness coefficient of the vibration isolator；
If the negative stiffness coefficient be greater than the vibration isolator stiffness coefficient, by the stiffness coefficient of the vibration isolator can value model
It encloses and reduces preset section from minimum, and determine that the new of stiffness coefficient of the vibration isolator can value range；
The vibration isolator stiffness coefficient it is new can minimalization in value range when, according to the first relational expression meter
Calculate the negative stiffness coefficient.
6. the method according to claim 1, wherein the method also includes:
Obtain branch suffered by the quantity of the vibration isolator below floating plate and the vibration isolator below the floating plate
Counter-force；
The damping of the controllable damping part is determined according to support reaction suffered by the quantity of the vibration isolator and the vibration isolator
Force parameter.
7. a kind of parameter determining device of vibration isolator, which is characterized in that the vibration isolator includes: positive rigidity elastic component, negative stiffness
Elastic component and controllable damping part；Described device includes:
First data acquisition module, described in being obtained according to the vibration isolator in the default largest deformation amount in vertical vibration direction
Just rigid coefficient；
Second data acquisition module, the initial length, the negative stiffness elastic component for obtaining the negative stiffness elastic component are in institute
State installation number in vibration isolator and when the vertical positive rigidity elastic component of the negative stiffness elastic component, the negative stiffness
The length of elastic component；
Module is constructed, for constructing the stiffness coefficient of the vibration isolator and the negative stiffness coefficient of the negative stiffness elastic component, described
The first relational expression that positive stiffness coefficient, the initial length, the installation number and the length determine；Wherein, the vibration isolation
The largest deformation amount in vertical vibration direction that the stiffness coefficient value of device should meet the vibration isolator is less than default largest deformation
Amount；
Parameter determination module, for the stiffness coefficient in the vibration isolator can minimalization in value range when, according to described
First relational expression calculates the negative stiffness coefficient.
8. a kind of ultralow frequency high-damping vibration isolator characterized by comprising positive rigidity elastic component, negative stiffness elastic component and controllable
Damping piece, wherein the negative stiffness coefficient of negative stiffness elastic component method as described in any one of claim 1-5 is true
It is fixed.
9. ultralow frequency high-damping vibration isolator according to claim 8, which is characterized in that the damping force of the controllable damping part
It is determined by method of claim 6.
10. a kind of track, which is characterized in that including rail, floating plate and ultralow frequency high-damping vibration isolation as claimed in claim 9
Device, the rail are set to above the floating plate, and are connect by fastener with the floating plate, the ultralow frequency high-damping
Vibration isolator is set to below the floating plate.
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| CN109902414B (en) | 2021-02-05 |
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