CN101338806A - Method for suppressing brake whistling - Google Patents
Method for suppressing brake whistling Download PDFInfo
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- CN101338806A CN101338806A CNA2007100526214A CN200710052621A CN101338806A CN 101338806 A CN101338806 A CN 101338806A CN A2007100526214 A CNA2007100526214 A CN A2007100526214A CN 200710052621 A CN200710052621 A CN 200710052621A CN 101338806 A CN101338806 A CN 101338806A
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Abstract
The present invention relates to a method for inhibiting a brake from squealing. The related brake is composed of a brake disc (38) or a brake drum, a brake block (26), a brake block steel backing (28), a brake driving force actuator such as a brake piston (22) or a brake caliper (24), and a particle damper (3). The brake is characterized in that the particle damper (3) is inserted between the brake driving force actuator and the brake block steel backing (28) or between the brake block steel backing (28) and the brake block (26) or between the brake driving force actuator and the brake block (26). Under the vibration, relative friction motion occurs among the tightly contacted particles (100) in the particle damper (3), and as a result, the particle damper (3) absorbs vibration energy within a bandwidth range between 0.1Hz and 15000Hz and along at least one DOF (degree of freedom) direction and inhibits the resonance peak and the squeals of the brake.
Description
Technical field
The present invention relates to a kind of method that suppresses brake whistling, relate to break and granule damper, especially high fill-ratio (more than or equal to 74%) granule damper, utilize the low advantage of big damping, dynamic rate relevant in the broad frequency range of existing high fill-ratio granule damper with excitation, it is little to have remedied existing break bloop damping function, working mechanism is fuzzy, and piezoelectricity chip bloop has reduced deficiencies such as the maximum brake power of vehicle, cost height, unfailing performance are under suspicion.
Technical background
The vehicle brake noise more and more causes the concern of people for environmental factor, and the relevant mandatory rules of law of country is put into effect.
Braking noise is divided into low frequency and high frequency, low frequency is positioned at 200Hz-500Hz, high frequency is uttered long and high-pitched sounds and is positioned at 1KHz-15KHz, and drum brake (the K.Brent Dunlap of Delphi Chassis System etc. that utter long and high-pitched sounds than disk type braker is easier, AnInvestigative Overview of Automobile Disk Brake Noise, SAE Technical Paper Series, Int.Congress and Exposition, 1999; Oliviero Giannini, Adnan Akay, the ExperimentalAnalysis of Brake Squeal Noise on a Laboratory Brake Setup of Francesco Massi, J.of Sound ﹠amp; Vibration, 292 (2006) 1-20).
Though brake whistling mainly ascribes the frictional vibration that characteristics of friction materials causes to, associated mechanical components and between coupling vibration, but owing to relate to transformation stress, become Sliding velocity, the alternating temperature degree, become humidity, the change rigidity of material and the change gap between coupled face, the influence of other factorses such as road excitation factor, the history of about a century has been experienced in research, the paper enormous amount, the related invention patent is arranged, and become one of world-famous puzzle (Chen Guangxiong, Zhou Zhongrong, " frictional noise present Research and the progress " of Xie Youbai, " friction journal ", the 20th the 6th phase of volume, in December, 2000; N.M.Kinkaid, O.M.O ' Reilly, the Automotive Disk Brake Squeal of P.Papadopoulos, J.of Sound and Vibration, 267 (2003) 105-166; " the friction catch Noise Prevention and Treatment progress " of yellow-study literary composition, Zhang Jinhuan, Dong Guangneng, Xie Youbai, " lubricated with sealing ", in November, 2006).
Two aspects are considered in present research emphatically: 1) materials science that relates at the frictional vibration between rubbing surface, tribology; 2) the coupling vibration that excitation causes at the frictional vibration between rubbing surface.But tended to the latter in recent years: the self oscillations mechanism that friction causes always.For this reason, U. S. Patent (US4235314 Non-Squeal Disc Brake, Nov.25,1980) has disclosed a kind of method that suppresses braking plate vibration, is that the elastic damping rubber elastomer is set in piston cavity, suppresses the vibration of braking plate and utters long and high-pitched sounds; U. S. Patent (US5842546, Split Backplate for Noise Suppression in Brake PadAssembles, Dec.1,1998) steel backing with braking plate is divided into three layers, accompany vibration damping viscoelasticity rubber body between tinsel, thereby can suppress braking noise and not need to transform the structure of brake calipers, the soft cotton sensation when also having eliminated hard brake down.Simultaneously, U. S. Patent (US6105736 Disk Brake and Anti-Squeal Shim Therefor, Aug.22,2000) disclosed a kind of bloop, both at the steel backing back pad one deck silencing pad that has braking plate now, this silencing pad is by the viscoelasticity rubber layer and sheet metal is two-layer forms, and its viscoelasticity rubber layer is installed in the face of brake-holder block steel-back, to suppress brake noise.China's vehicle uses maximum still this or its improved products at present, does not find relevant Chinese invention patent and application yet.
Different therewith is, in steel backing back that has braking plate now or piston cavity, install a kind of piezoelectric ceramic additional, utilization is far above high frequency vibrating signal (Fast Vibration) the excitation braking plate of brake whistling frequency, thereby eliminate the non-linear factor of drag friction power, level and smooth frictional force is uttered long and high-pitched sounds thereby eliminate.
This technique functions comes from and solves creeping that mechanical structure is in operation, as superposition high frequency vibrating signal in the hydraulic proportional valve control signal, eliminate the frictional force of hydraulic proportional and selector valve, J.J.Thomsen (SomeGeneral Effects of Strong High-frequency Excitation:Stiffening as solid mechanics system of Denmark University of Science and Technology, Biasing andSmoothening, J.of Sound ﹠amp; Vibration (2002) 253 (4), 807-831); The practice and discover that the frictional force between its supporting and ground can be significantly cut down in the vibrational excitation of barrel roll laundry machine in the drying program, thereby cause barrel roll laundry machine free on the ground migration under the effect of small side direction unbalanced force; Compressor in running order is also usually owing to this problem is moved about; So, research is not difficult to find, use the improper maximum braking force that can make of piezoelectric ceramic to decline to a great extent, cause a hidden trouble to brake safe, J.J.Thomsen (Using Fast Vibrations to QuenchFriction-Induced Oscillation, J.of Sound ﹠amp as solid mechanics system of Denmark University of Science and Technology; Vibration (1999) 228 (5), 1079-1102; ) just spell out this problem, the S.Chatterjee of India Deemed university, T.K.Singha, S.K.Karmakar, (Non-Trivial Effect of Fast Vibration on the Dynamicsof a Class of Non-linearly Damped Mechanical System, J.of Sound ﹠amp on the basis that flutter is fully studied for high frequency; Vibration260 (2003), 711-730) announcement high frequency flutter (Fast Vibration) is opposite for the effect of the low speed damping of the braking plate of different hardness; Simultaneously, same authors (Effect of High-Frequency Excitation on a Class ofMechanical Systems with Dynamic friction, J.of Sound ﹠amp; Vibration 269 (2004) 61-89) provide lot of data demonstration, high frequency flutter that frictional force is reduced.
Efficient ways is at present, on the basis of disregarding mechanical structure rigidity, matching gap and structure coupling vibration, the measure that is widely used in suppressing brake whistling is: be provided with or composite damping material at the braking plate back side, as damping rubber layer or bloop, so that the frictional vibration that suppresses between rubbing surface encourages.At this point, the Zhang Fang of Tsing-Hua University, Guan Dihua (" suppressing the discussion of the damping method of break vibration noise ", " automotive engineering ", 2003 the 25th the 3rd phases of volume, 264 pages-268 pages) carried out specially pointing out after the discussion: though the break product of damping layer structure was just put on market as far back as the eighties in 20th century, its true usefulness generally will lean on trial test repeatedly to hold, and is not only consuming time, expensive, and depend on artificer's experience; Simultaneously, this processing method is not always effective; The friction usefulness of damping layer between junction plane is high more, and the effect that can reach the unstable mode that exists in the inhibition structure is good more; After introducing the damping of viscoelastic material, may introduce new destabilizing factor in the system, thereby adopt the method inhibition brake whistling of visco-elastic damping layer may not be suitable for all breaks.
Practical experience shows that when introducing high damping, it is possible reducing the dynamic rate in the micron order vibration control as far as possible and suppressing dither.
Though adopt existing vibration isolation technique can effectively avoid the resonance peak of controlling object, realize effective vibration isolation in the vibration isolation district, the transmissibility at intrinsic peak value place is excessive, and is very dangerous during by resonant frequency.As at the natural frequency place, the transmissibility of metal spring vibration isolator is accompanied greater than 50, can only good result be arranged in the vibration isolation district greater than frequency ratio 1.414; At the natural frequency place, the transmissibility of rubber vibration isolator is that 6-10 accompanies, and the transmissibility of big damping viscoelastic material is that 3-4 accompanies; At the natural frequency place, the transmissibility of steel-wire isolator is 3 to accompany, and faces permanent deformation, fatigue fracture and breakdown problem; The coulomb friction vibration isolator of function admirable can not have intrinsic peak, but easy slippage and instability.Obviously, existing vibration isolation technique is difficult to satisfy engineering and life application.
Utilize damping vibration damping effectively, utilize proper effect obvious; The adaptation frequency of frictional damping is wide, and especially the particle frcition damper is called as the broad band damp device, have in addition be operated in severally to tens Kilohertzs, this is that most of dampers institute is incompetent, thereby is widely used." steamed buns stuffed with sweetened bean paste damper " (" aviation journal " as Li Wei etc., in March, 1999), the Investigating Particle Impact Damping As a Means of FatigueReduction (9th Joint FAA/DoD/NASA Aging Aircraft Conference) of VikramK.Kinra and Bryan Witt, Design Methodology for Particle Damping (the Smart Structures and Materials:Damping andIsolation Newport Beach of Bryce L.Fowler etc., CA, March 2001), " based on the inertial platform three-dimensional vibration isolator of friction energy-dissipating mechanism " (" the noise and vibration control " of the long vessel used to hold grain at the imperial sacrifice of Lee of Henan Electromechanical higher junior college, in August, 1997) and " particle damping isolator " (machinery, 1998 the 25th volume supplementary issue), Japan Patent JP2001355672 (Particle Vibration_IsolatingDamper), U.S. Pat 6260676 B1 (Magnetic Particle Damper Apparatus), US6547049 (Particle Vibration Damper), US6802405 B2 (Friction Vibration Damper), US2006/0180420A1 (Vibration Damper) and US20070012530 A1 (Bearing Damper Having Dispersed FrictionDamping Elements).
Wherein, " the steamed buns stuffed with sweetened bean paste damper " of Li Wei etc. though also flexible constraint, the rigidity of its elastic material is too little, thereby can not bear the action of gravity of controlled device or pretightening force correspondingly, and can not be used to support controlled device; Secondly, adopt the purpose of little rigidity to be, take place in the working procedure of permission " steamed buns stuffed with sweetened bean paste damper " to collide between particle, implement the exchange of collision energy.This is that intergranular collision is of equal importance with friction because diffussion and energy exchange and frictional energy exchange are in the same order of magnitude; Simultaneously, in this paper, as other granule damper, " steamed buns stuffed with sweetened bean paste damper " also is to be attached on " body " of controlled object, vibrate with controlled device, thereby utilize the exchange of intergranular diffussion and energy exchange and frictional energy, be not arranged between side support and the controlled device, also do not exert pressure by side support and controlled device.
The Investigating Particle Impact Damping As a Meansof Fatigue Reduction (9 of Vikram K.Kinra and Bryan Witt
ThJoint FAA/DoD/NASA Aging Aircraft Conference) utilizes the terminal attaching particles damper of overhanging beam, in overhang and attaching particles damper vibrate together, the fill factor of granule damper and the relation between the terminal immeasurable firm damping constant of described overhanging beam have been studied.Show raising along with fill factor, the space that particle moves mutually diminishes, almost there is not relative movement between particle when filling greater than 80%, thereby the kinetic energy of particle disappears, and does not have the exchange of intergranular collision and energy, does not almost have damping function (unless there is nonuniformity in grain graininess), this is similar to wideband particle dynamic vibration absorber, obviously, for dynamic vibration absorber was used, intergranular collision seemed important than intergranular friction.
" based on the inertial platform three-dimensional vibration isolator of friction energy-dissipating mechanism " (" the noise and vibration control " of the long vessel used to hold grain at the imperial sacrifice of Lee of Henan Electromechanical higher junior college, in August, 1997), its action principle is to insert friction lever in the cavity of its granule damper, the mobile variation that can not cause the granule damper cavity volume of pole, pressure ring same up and down moved further under the effect of spring up and down, thereby can not push for particle wherein, described granule damper cavity can not hold the effect of supporting force comprehensively.
U.S. Pat 6260676 B1 (Magnetic Particle Damper Apparatus) implement damping function by the working stress between magnetic field control magnetic-particle, and think that the alternative of MR damper is also superior; Do not have flexible cavity, can not be used to bear the gravity of controlled device or pretightening force correspondingly;
U.S. Pat 2006/0180420 A1 (Vibration Damper) is then under the cavity volume situation less than filling and immobilized particles damper, inflation being set in the variation by electromagnetic field, gas-filled cavity volume, the granule damper reservoir body in floating piston, the granule damper cavity volume controlling and the intergranular active force of adjustment movement, obviously also is attached to playing vibration with one on the controlled device.
U.S. Pat 6802405 B2 (Friction Vibration Damper) are provided with a shelves stream plate in the granule damper of complete filling not, suppress the damping vibration attenuation effect of granule damper.
The granule damper of Japan Patent JP2001355672 (Particle Vibration_Isolating Damper) by the cavity of granule damper, in the cavity particle, be arranged in cavity the driving floating piston all portion, be positioned at the granule damper cavity and form with the piston rod etc. that is connected of outer end; Its material that constitutes the granule damper cavity is generally rigid body, the moving up and down of rigid piston rod makes (' energydissipation due to a collision of the particle filled around the float ' that changes and bump of the intergranular extrusion stress in the granule damper cavity after the abundant filling
Draw from esp@cenetDatabase), the motion of friction piston almost can not cause the variation of granule damper cavity volume; Admit directly load-bearing in the patent, obviously have sizable extrusion stress between its inner particle under this operating mode, this helps the friction energy-dissipating effect between enhanced granule.Obviously its structure complicated is not suitable for the extensive use on mini-plant especially movable equipment.
US20070012530 A1 (Bearing Damper Having Dispersed Friction Damping Elements) then is the high temperature modification granule damper that proposes for the vibration damping of motive bearing specially, and is as follows to this patent analyses:
1) this patent is emphasized its granule damper cavity complete filling;
2) because the support stiffness of rotor-support-foundation system is very big, often can not utilize elastic vibration isolation; Its granule damper housing adopts the stainless steel metal material, in the course of the work in radial-deformation very little (... that can flex somewhatin the radial direction of the bearing.---draws from this patent), its stiffness coefficient is big, should the vibration isolation requirement of the removable instrument and equipment of vibration damping again thereby can not be used for; Because vibration isolation is that its stiffness coefficient is little for the requirement of system, to reduce the natural frequency of supporting, avoid energizing frequency, and vibration damping is that must there be damping in system, to suppress intrinsic peak value for the requirement of system;
3) shape of this damper cavity is to be enclosed within the outer ring-shaped cavity of bearing, after filling and installing, under the effect of gravity, in state of rest one side distortion is only arranged, and in rotor rotation process, for dynamic balancing rotor-support-foundation system preferably, centrifugal force is very little, thereby be difficult to realize while compressive strain for granule damper on other orientation, thereby make the working stress between its internal particle very little, thereby utilize the catabiotic effect of intergranular phase mutual friction very little;
4) shape of this damper cavity is to be enclosed within the outer ring-shaped cavity of bearing, after filling and installing, under the effect of gravity, in state of rest the distortion of one side is only arranged, and in rotor rotation process, if dynamic balancing is bad, centrifugal force is very big, be analogous to quiet, the dynamic pressure support bearing is the same, centrifugal power will impel the particle whirling motion with the whirling motion of axle in the cavity, thereby be difficult to realize while compressive strain for granule damper on other orientation, in case there is not pressure to fill, working stress between its internal particle is little, thereby utilizes the catabiotic effect of intergranular phase mutual friction little;
5) but this patent also disclosed in described granule damper cavity and to have added the pressurising cavity, so that by extraneous hydrodynamic pressure, control the tightness degree of particle in the described granule damper cavity, thereby realize adjusting for damping, as seen, though adopt metal shell that the operating temperature of granule damper is improved, because the rigidity of metal is big, fill thereby can apply pretightening force, have to adopt the method for additive fluid cavity to solve unlike the elastic caoutchouc shells;
6) under the unidimensional prerequisite, obviously the manufacturing cost height of profiled metal housing can not be used for such as the vehicle brake vibration damping, because very responsive for cost;
7) simultaneously, because the product for civilian use is cheap for will the rectificating of working life, thereby because the fatigue strength of metal is low, the processing cost height is difficult to be applied to the vibration control of brake, motor and the operator cabin of vehicle etc.
Can deposit a kind of by braking technique, the A) practical difficulty that mates of the rigidity that can overcome existing viscoelastic material and damping; B) can overcome the loss of properties on aging that has viscoelastic material now; C) can overcome the heat resistance deficiency that has viscoelastic material now; D) can overcome the existing viscoelastic material ability that is squeezed; E) can overcome the vibration damping of existing viscoelastic material and the problem that the inhibition ability of uttering long and high-pitched sounds can be differed from by vibration frequency restriction and broad applicability; F) can overcome the existing big shortcoming of viscoelastic material dynamic rate; G) can overcome existing high frequency, the small magnitude flutter causes the safety hazard that maximum braking force reduces, and frictional force is tended towards stability sliding-glue when occurring; H) improve therebetween unfailing performance and for the tolerance of processing, assembly error.
Here it is pushes granule damper.Simultaneously, above analysis shows, also granule damper is not applied to suppress the precedent of brake whistling, engine vibration isolation so far, granule damper is not used for transferring power and break vibration control under the extruding force effect especially.And adopt granule damper to suppress the purpose that brake whistling should be invented just.
Summary of the invention
In order to achieve the above object, the present invention has disclosed a kind of method that suppresses brake whistling, relates to brake disc 38 in the break or brake drum, braking plate 26, brake-holder block steel-back 28, braking and drive force final controlling element such as brake piston 22 or brake calipers 24, granule damper 3; It is characterized in that: 28 of braking and drive force final controlling element and brake-holder block steel-backs, or 26 of brake-holder block steel-back 28 and braking plates, or braking and drive force final controlling element and 26 of braking plates insert granule damper 3; Described granule damper 3 is to be combined by airtight flexible cavity 5 and particle 100; Be filled with described particle 100 in the described airtight flexible cavity 5, described particle 100 is in tight contact condition with the internal face of described airtight flexible cavity 5; The material of forming this flexible cavity comprises various rubber, plastics, compound, the various lamination coating of rubber and plastic or the above elastomer that is mixed and made into, perhaps respectively or multiple mixing back with metal composite or combine, perhaps this flexible cavity all is made up of metal thin-wall; The main effect of this airtight flexible cavity 5 is: contain described particle 100, under the applied load effect, resiliently deformable by this flexible cavity, keeping the applied load working stress can be applied between wherein particle, in supporting applied load, transferring power, improve the frictional force of relative movement between intergranular working stress and particle, and particle relative position is wherein resetted; Described particle 100 is contained in the described airtight flexible cavity 5, and it mainly acts on and is: adding under the working stress effect, utilizing described intergranular mutual rubbing action, provide frictional damping to vibration system in broad frequency range, suppressing resonance peak; In actual the use, working stress makes airtight flexible cavity 5 resiliently deformables of described granule damper 3, and wherein intergranular contact pressure stress increases and is in tight contact condition; Under oscillating action, relative fricting movement appears in 100 of particles that are in the described granule damper 3 under the tight contact condition, thereby in 0.1～15000Hz broadband range and at least, on the one degree of freedom direction, consume vibrational energy, suppress resonance peak and suppress brake whistling.
Technical measures
Concrete technical measures are:
A kind of method that suppresses brake whistling relates to brake disc 38 in the break or brake drum, braking plate 26, brake-holder block steel-back 28, braking and drive force final controlling element such as brake piston 22 or brake calipers 24, granule damper 3; It is characterized in that: 28 of braking and drive force final controlling element and brake-holder block steel-backs, or 26 of brake-holder block steel-back 28 and braking plates, or braking and drive force final controlling element and 26 of braking plates insert granule damper 3; Described granule damper 3 is to be combined by airtight flexible cavity 5 and particle 100; Be filled with described particle 100 in the described airtight flexible cavity 5, described particle 100 is in tight contact condition with the internal face of described airtight flexible cavity 5; The material of forming this flexible cavity comprises various rubber, plastics, compound, the various lamination coating of rubber and plastic or the above elastomer that is mixed and made into, perhaps respectively or multiple mixing back with metal composite or combine, perhaps this flexible cavity all is made up of metal thin-wall; The main effect of this airtight flexible cavity 5 is: contain described particle 100, under the applied load effect, resiliently deformable by this flexible cavity, keeping the applied load working stress can be applied between wherein particle, in supporting applied load, transferring power, improve the frictional force of relative movement between intergranular working stress and particle, and particle relative position is wherein resetted; Described particle 100 is contained in the described airtight flexible cavity 5, and it mainly acts on and is: adding under the working stress effect, utilizing described intergranular mutual rubbing action, provide frictional damping to vibration system in broad frequency range, suppressing resonance peak; In actual the use, working stress makes airtight flexible cavity 5 resiliently deformables of described granule damper 3, and wherein intergranular contact pressure stress increases and is in tight contact condition; Under oscillating action, relative fricting movement appears in 100 of particles that are in the described granule damper 3 under the tight contact condition, thereby in 0.1～15000Hz broadband range and at least, on the one degree of freedom direction, consume vibrational energy, suppress resonance peak and suppress brake whistling.
Described a kind of method that suppresses brake whistling is characterized in that, the particle size range of the particle 100 in the described granule damper 3 is from 0.00001 micron to 5 millimeters.
Described described a kind of method that suppresses brake whistling, it is characterized in that, particle 100 in the described granule damper 3 is that the monomer with certain pattern, single distribution diameter granular material of planting are formed, as metal granule lead, wolfram steel, steel, iron, aluminium, copper etc., as nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, starch, elastomer particles etc.
Described a kind of method that suppresses brake whistling, it is characterized in that, particle 100 in the described granule damper 3 is that the granular material of the monomer with certain pattern, multiple distribution diameter is formed, as metal granule lead, wolfram steel, steel, iron, aluminium etc., as nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, elastomer particles etc.
Described a kind of method that suppresses brake whistling, it is characterized in that, particle 100 in the described granule damper 3 is that many bodies with certain pattern, single distribution diameter granular material of planting are formed, as metal granule lead, wolfram steel, steel, iron, aluminium etc. or and the mixture of nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, elastomer particles etc.
Described a kind of method that suppresses brake whistling, it is characterized in that, particle 100 in the described granule damper 3 is that the granular material with many bodies of certain pattern, multiple distribution diameter is formed, as metal granule lead, wolfram steel, steel, iron, aluminium etc. or and the mixture of nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, elastomer particles etc.
Described a kind of method that suppresses brake whistling is characterized in that, particle 100 surfaces in the described granule damper 3 can application rust preventing agent layer; Described rust preventing agent layer protection particle non-corrosive.
Described a kind of method that suppresses brake whistling is characterized in that, particle 100 surfaces in the described granule damper 3 can application increase the agent layer that rubs; The described agent layer that rubs that increases is used to improve intergranular friction factor, improves the frictional damping coefficient.
Description of drawings
Figure of description is as follows:
Fig. 1 is a kind of schematic representation of vehicle disc brake;
Fig. 2 is a kind of structural representation of vehicle disc brake braking plate;
Fig. 3 is a kind of schematic representation of vehicle drum brake;
Fig. 4 is a kind of schematic representation of vehicle drum brake braking plate;
Fig. 5 is a kind of braking plate structural representation that has bloop;
Fig. 6 is a kind of braking plate structure 1 schematic representation that replaces existing bloop with granule damper;
Fig. 7 is a kind of braking plate structure 2 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper;
Fig. 8 is a kind of braking plate structure 3 schematic representation that replace existing bloop with granule damper;
Fig. 9 is a kind of braking plate structure 4 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper;
Figure 10 is a kind of braking plate structure 5 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper;
Figure 11 is a kind of braking plate structure 6 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper;
Figure 12 is a kind of braking plate structure 7 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper;
Figure 13 is a kind of braking plate structure 8 schematic representation that replace existing bloop with granule damper;
Figure 14 is a kind of braking plate structure 9 schematic representation that replace existing bloop with granule damper;
Figure 15 is a kind of braking plate structure 10 schematic representation that replace existing bloop with granule damper;
Embodiment
Below with reference to Fig. 1-Figure 15 in detail a kind of method that suppresses brake whistling is described in detail:
Fig. 1 is a kind of schematic representation of vehicle disc brake, and the bloop that it is formed by support 20, brake calipers 24, braking and drive force final controlling element such as brake piston 22, by steel disc 32 and viscoelastic body 30, brake-holder block steel-back 28, braking plate 26 etc. are formed.In cavity 36 under the hydrodynamic pressure P effect, braking and drive force final controlling element such as brake piston 22 or brake calipers 24 by bloop compress brake-holder block steel-back, this steel backing presses braking plate 26, this braking plate presses brake disc 38, implements braking for brake disc 38.In the braking process, because the cunning between braking plate and brake disc-sticking effect, being that therebetween frictional force is unstable and cause frictional vibration, is because the self oscillations that friction causes is consequently braked high frequency and uttered long and high-pitched sounds.
Generally speaking, a cavity 34 of described brake piston 22 is a cavity body.
Fig. 2 is a kind of structural representation of vehicle disc brake braking plate, and generally speaking, braking plate and brake-holder block steel-back are for being fastenedly connected.
As Fig. 3 is a kind of schematic representation of vehicle drum brake, and its side view is Fig. 4;
Fig. 5 is a kind of braking plate structural representation that has bloop, and generally speaking this bloop can be compound with brake-holder block steel-back (28), also can use separately; Documents and materials show that the effect of this bloop is, when the braking plate flexure vibrations, utilizes the distortion consumption of viscoelastic material, thereby suppress brake squeal.
A kind of method that suppresses brake whistling relates to brake disc 38 in the break or brake drum, braking plate 26, brake-holder block steel-back 28, braking and drive force final controlling element such as brake piston 22 or brake calipers 24, granule damper 3; It is characterized in that: 28 of braking and drive force final controlling element and brake-holder block steel-backs, or 26 of brake-holder block steel-back 28 and braking plates, or braking and drive force final controlling element and 26 of braking plates insert granule damper 3; Described granule damper 3 is to be combined by airtight flexible cavity 5 and particle 100; Be filled with described particle 100 in the described airtight flexible cavity 5, described particle 100 is in tight contact condition with the internal face of described airtight flexible cavity 5; The material of forming this flexible cavity comprises various rubber, plastics, compound, the various lamination coating of rubber and plastic or the above elastomer that is mixed and made into, perhaps respectively or multiple mixing back with metal composite or combine, perhaps this flexible cavity all is made up of metal thin-wall; The main effect of this airtight flexible cavity 5 is: contain described particle 100, under the applied load effect, resiliently deformable by this flexible cavity, keeping the applied load working stress can be applied between wherein particle, in supporting applied load, transferring power, improve the frictional force of relative movement between intergranular working stress and particle, and particle relative position is wherein resetted; Described particle 100 is contained in the described airtight flexible cavity 5, and it mainly acts on and is: adding under the working stress effect, utilizing described intergranular mutual rubbing action, provide frictional damping to vibration system in broad frequency range, suppressing resonance peak;
Fig. 6 is a kind of braking plate structure 1 schematic representation that replaces existing bloop with granule damper; This granule damper 3 is made up of flexible cavity 5, particle 100; The airtight cavity 5 that wherein said flexible cavity 5 is composited by steel plate and viscoelastic material respectively, wherein said viscoelastic material is near brake-holder block steel-back 28; This granule damper 3 can use separately or be combined with each other with described brake-holder block steel-back 28; Described granule damper 3 can be between braking and drive force final controlling element such as brake piston 22 and brake-holder block steel-back 28, or between brake calipers 24 and the brake-holder block steel-back 28;
Fig. 7 is a kind of braking plate structure 2 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper; This granule damper 3 forms airtight cavity 5 by steel plate and particle 100 is formed, and directly and braking plate be fastenedly connected, thereby cancelled brake-holder block steel-back and existing bloop; Described granule damper 3 can be between braking and drive force final controlling element such as brake piston 22 and braking plate 26, or between brake calipers 24 and the braking plate 26;
Fig. 8 is a kind of braking plate structure 3 schematic representation that replace existing bloop with granule damper; This granule damper 3 is made up of flexible cavity 5, particle 100; The airtight cavity 5 that wherein said flexible cavity 5 viscoelastic materials form is being compounded with steel plate by braking and drive force final controlling element one side, and one improves extrusion capability, and wherein said viscoelastic material is near brake-holder block steel-back 28; This granule damper 3 can use separately or be combined with each other with described brake-holder block steel-back 28; Described granule damper 3 can be between braking and drive force final controlling element such as brake piston 22 and brake-holder block steel-back 28, or between brake calipers 24 and the brake-holder block steel-back 28;
Fig. 9 is a kind of braking plate structure 2 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper; This granule damper 3 forms airtight cavity 5 by two-layered steel plates by the peripheral compound seal of viscoelastic material and particle 100 is formed, and directly and braking plate be fastenedly connected, thereby cancelled brake-holder block steel-back and existing bloop; Described granule damper 3 can be between braking and drive force final controlling element such as brake piston 22 and braking plate 26, or between brake calipers 24 and the braking plate 26;
Figure 10 is a kind of braking plate structure 2 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper; This granule damper 3 forms airtight cavity 5 by two-layered steel plates by the viscoelastic material compound seal and particle 100 is formed, and directly and braking plate be fastenedly connected, thereby cancelled brake-holder block steel-back and existing bloop; Wherein, described viscoelastic material forms reticular structure between two steel plates; Described granule damper 3 can be between braking and drive force final controlling element such as brake piston 22 and braking plate 26, or between brake calipers 24 and the braking plate 26;
Figure 11 is a kind of braking plate structure 2 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper; This granule damper 3 is made up of airtight cavity 5 and particle 100 that braking plate and brake-holder block steel-back are composited respectively; Described granule damper 3 can be between braking and drive force final controlling element such as brake piston 22 and braking plate 26, or between brake calipers 24 and the braking plate 26;
Figure 12 is a kind of braking plate structure 2 schematic representation that replace existing bloop and existing brake-holder block steel-back with granule damper; This granule damper 3 is made up of airtight cavity 5 of segmentation and particle 100 that braking plate and brake-holder block steel-back are composited respectively; Described granule damper 3 can be between braking and drive force final controlling element such as brake piston 22 and braking plate 26, or between brake calipers 24 and the braking plate 26;
Figure 13 is a kind of braking plate structure 8 schematic representation that replace existing bloop with granule damper; This granule damper 3 is made up of flexible cavity 5, particle 100; The elastic sealing cavity 5 of the variable-volume that the cavity 34 of its middle section bow shaped steel plate and described braking and drive force final controlling element such as brake piston 22 is formed, the bow shaped steel plate outside, wherein said cross section can be compounded with viscoelastic material and near brake-holder block steel-back 28;
Figure 14 is a kind of braking plate structure 9 schematic representation that replace existing bloop with granule damper; This granule damper 3 is made up of flexible cavity 5, particle 100; The elastic sealing cavity 5 of the variable-volume that the cavity 34 of its middle section inverted U viscoelastic material and described braking and drive force final controlling element such as brake piston 22 is formed;
Figure 15 is a kind of braking plate structure 10 schematic representation that replace existing bloop with granule damper; This granule damper 3 is made up of flexible cavity 5, particle 100; The steel plate of its middle section type of falling Ω and viscoelastic material are combined into elastic sealing cavity 5; This granule damper 3 described braking and drive force final controlling element as brake piston 22 and as described between the brake-holder block steel-back.
In actual the use, working stress makes airtight flexible cavity 5 resiliently deformables of described granule damper 3, and wherein intergranular contact pressure stress increases and is in tight contact condition; Under oscillating action, relative fricting movement appears in 100 of particles that are in the described granule damper 3 under the tight contact condition, thereby in 0.1～15000Hz broadband range and at least, on the one degree of freedom direction, consume vibrational energy, suppress resonance peak and suppress brake whistling.
Described a kind of method that suppresses brake whistling is characterized in that, the particle size range of the particle 100 in the described granule damper 3 is from 0.00001 micron to 5 millimeters.
Described described a kind of method that suppresses brake whistling, it is characterized in that, particle 100 in the described granule damper 3 is that the monomer with certain pattern, single distribution diameter granular material of planting are formed, as metal granule lead, wolfram steel, steel, iron, aluminium, copper etc., as nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, starch, elastomer particles etc.
Described a kind of method that suppresses brake whistling, it is characterized in that, particle 100 in the described granule damper 3 is that the granular material of the monomer with certain pattern, multiple distribution diameter is formed, as metal granule lead, wolfram steel, steel, iron, aluminium etc., as nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, elastomer particles etc.
Described a kind of method that suppresses brake whistling, it is characterized in that, particle 100 in the described granule damper 3 is that many bodies with certain pattern, single distribution diameter granular material of planting are formed, as metal granule lead, wolfram steel, steel, iron, aluminium etc. or and the mixture of nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, elastomer particles etc.
Described a kind of method that suppresses brake whistling, it is characterized in that, particle 100 in the described granule damper 3 is that the granular material with many bodies of certain pattern, multiple distribution diameter is formed, as metal granule lead, wolfram steel, steel, iron, aluminium etc. or and the mixture of nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, elastomer particles etc.
Obviously, for the colleague technician, this invention not only is confined to structural type and its method of above announcement.Simultaneously, the cross-section structure form of described granule damper is not limited to break, and can be applied to the field of other supporting and vibration damping, as the motor high-frequency vibration isolation, and washing machine leg etc., these all should belong to this Patent right protection domain.
Claims (8)
1, a kind of method that suppresses brake whistling relates to brake disc (38) in the break or brake drum, braking plate (26), brake-holder block steel-back (28), braking and drive force final controlling element such as brake piston (22) or brake calipers (24), granule damper (3); It is characterized in that: between braking and drive force final controlling element and brake-holder block steel-back (28), or between brake-holder block steel-back (28) and braking plate (26), or insert granule damper (3) between braking and drive force final controlling element and braking plate (26); Described granule damper (3) is to be combined by airtight flexible cavity (5) and particle (100); Be filled with described particle (100) in the described airtight flexible cavity (5), described particle (100) is in tight contact condition with the internal face of described airtight flexible cavity (5); The material of forming this flexible cavity comprises various rubber, plastics, compound, the various lamination coating of rubber and plastic or the above elastomer that is mixed and made into, perhaps respectively or multiple mixing back with metal composite or combine, perhaps this flexible cavity all is made up of metal thin-wall; The main effect of this airtight flexible cavity (5) is: contain described particle (100), under the applied load effect, resiliently deformable by this flexible cavity, keeping the applied load working stress can be applied between wherein particle, in supporting applied load, transferring power, improve the frictional force of relative movement between intergranular working stress and particle, and particle relative position is wherein resetted; Described particle (100) is contained in the described airtight flexible cavity (5), it mainly acts on: adding under the working stress effect, utilize described intergranular mutual rubbing action, in broad frequency range, provide frictional damping, suppress resonance peak to vibration system; In actual the use, working stress makes airtight flexible cavity (5) resiliently deformable of described extruding granule damper (3), and wherein intergranular contact pressure stress increases and is in tight contact condition; Under oscillating action, be in the described granule damper (3) and occur relative fricting movement between the particle (100) under the tight contact condition, thereby in 0.1～15000Hz broadband range and at least, on the one degree of freedom direction, consume vibrational energy, suppress resonance peak and suppress brake whistling.
2, a kind of method that suppresses brake whistling according to claim 1 is characterized in that, the particle size range of the particle (100) in the described granule damper (3) is from 0.00001 micron to 5 millimeters.
3, according to the described described a kind of method that suppresses brake whistling of claim 1, it is characterized in that, particle (100) in the described granule damper (3) is that the monomer with certain pattern, single distribution diameter granular material of planting are formed, as metal granule lead, wolfram steel, steel, iron, aluminium, copper etc., as nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, starch, elastomer particles etc.
4, described a kind of method that suppresses brake whistling according to claim 1, it is characterized in that, particle (100) in the described granule damper (3) is that the granular material of the monomer with certain pattern, multiple distribution diameter is formed, as metal granule lead, wolfram steel, steel, iron, aluminium etc., as nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, elastomer particles etc.
5, described a kind of method that suppresses brake whistling according to claim 1, it is characterized in that, particle (100) in the described granule damper (3) is that many bodies with certain pattern, single distribution diameter granular material of planting are formed, as metal granule lead, wolfram steel, steel, iron, aluminium etc. or and the mixture of nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, elastomer particles etc.
6, described a kind of method that suppresses brake whistling according to claim 1, it is characterized in that, particle (100) in the described granule damper (3) is that the granular material with many bodies of certain pattern, multiple distribution diameter is formed, as metal granule lead, wolfram steel, steel, iron, aluminium etc. or and the mixture of nonmetallic material silica, thickness sand, mica, carbon dust, silicious marl, molecular sieve, elastomer particles etc.
7, described a kind of method that suppresses brake whistling according to claim 1 is characterized in that, particle (100) surface in the described granule damper (3) can application rust preventing agent layer; Described rust preventing agent layer protection particle non-corrosive.
8, described a kind of method that suppresses brake whistling according to claim 1 is characterized in that, particle (100) surface in the described granule damper (3) can application increase the agent layer that rubs; The described agent layer that rubs that increases is used to improve intergranular friction factor, improves the frictional damping coefficient.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2007100526214A CN101338806A (en) | 2007-07-03 | 2007-07-03 | Method for suppressing brake whistling |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2007100526214A CN101338806A (en) | 2007-07-03 | 2007-07-03 | Method for suppressing brake whistling |
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| CN101338806A true CN101338806A (en) | 2009-01-07 |
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| CNA2007100526214A Pending CN101338806A (en) | 2007-07-03 | 2007-07-03 | Method for suppressing brake whistling |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010261585A (en) * | 2009-04-09 | 2010-11-18 | Kobe Steel Ltd | Damping structure |
| CN102483115A (en) * | 2009-06-15 | 2012-05-30 | Itt制造企业公司 | Brake plate |
| CN104632986A (en) * | 2014-12-22 | 2015-05-20 | 西安交通大学 | Coupled electromagnetic field particle damper with ferromagnetic end cover additionally arranged at one end and vibration reduction method of particle damper for vibration structure |
| CN109709869A (en) * | 2019-01-14 | 2019-05-03 | 北京工业大学 | A kind of soft brake control method of control system |
| CN113700794A (en) * | 2021-05-25 | 2021-11-26 | 北京化工大学 | Damper suitable for rotor bearing system |
| US11215235B2 (en) | 2017-03-07 | 2022-01-04 | Siemens Aktiengesellschaft | Coupling element having vibration damping |
-
2007
- 2007-07-03 CN CNA2007100526214A patent/CN101338806A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010261585A (en) * | 2009-04-09 | 2010-11-18 | Kobe Steel Ltd | Damping structure |
| CN102388234A (en) * | 2009-04-09 | 2012-03-21 | 株式会社神户制钢所 | Vibration damping structure |
| CN102388234B (en) * | 2009-04-09 | 2013-10-16 | 株式会社神户制钢所 | Vibration damping structure |
| CN102483115A (en) * | 2009-06-15 | 2012-05-30 | Itt制造企业公司 | Brake plate |
| CN104632986A (en) * | 2014-12-22 | 2015-05-20 | 西安交通大学 | Coupled electromagnetic field particle damper with ferromagnetic end cover additionally arranged at one end and vibration reduction method of particle damper for vibration structure |
| US11215235B2 (en) | 2017-03-07 | 2022-01-04 | Siemens Aktiengesellschaft | Coupling element having vibration damping |
| CN109709869A (en) * | 2019-01-14 | 2019-05-03 | 北京工业大学 | A kind of soft brake control method of control system |
| CN113700794A (en) * | 2021-05-25 | 2021-11-26 | 北京化工大学 | Damper suitable for rotor bearing system |
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Open date: 20090107 |