CN105202096A - Suspension shock absorber adopting directional rotating flow self-adaptive liquid damping - Google Patents
Suspension shock absorber adopting directional rotating flow self-adaptive liquid damping Download PDFInfo
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- CN105202096A CN105202096A CN201510578123.8A CN201510578123A CN105202096A CN 105202096 A CN105202096 A CN 105202096A CN 201510578123 A CN201510578123 A CN 201510578123A CN 105202096 A CN105202096 A CN 105202096A
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- 238000013016 damping Methods 0.000 title claims abstract description 79
- 239000007788 liquid Substances 0.000 title abstract description 19
- 230000035939 shock Effects 0.000 title abstract description 9
- 239000000725 suspension Substances 0.000 title abstract description 7
- 239000006096 absorbing agent Substances 0.000 title abstract description 6
- 239000012530 fluid Substances 0.000 claims abstract description 79
- 230000007246 mechanism Effects 0.000 claims abstract description 31
- 229920001971 elastomer Polymers 0.000 claims abstract description 23
- 239000000806 elastomer Substances 0.000 claims abstract description 15
- 230000007306 turnover Effects 0.000 claims description 17
- 230000008878 coupling Effects 0.000 claims description 10
- 238000010168 coupling process Methods 0.000 claims description 10
- 238000005859 coupling reaction Methods 0.000 claims description 10
- 230000005855 radiation Effects 0.000 claims description 9
- 230000015572 biosynthetic process Effects 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 12
- 239000012528 membrane Substances 0.000 abstract description 4
- 238000010521 absorption reaction Methods 0.000 abstract 3
- 238000005192 partition Methods 0.000 abstract 3
- 230000002035 prolonged effect Effects 0.000 abstract 1
- 238000000034 method Methods 0.000 description 16
- 230000008569 process Effects 0.000 description 15
- 208000034189 Sclerosis Diseases 0.000 description 8
- 238000006243 chemical reaction Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 6
- 230000033001 locomotion Effects 0.000 description 5
- 230000001133 acceleration Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000005562 fading Methods 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 238000003756 stirring Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000033558 biomineral tissue development Effects 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000013178 mathematical model Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000002834 transmittance Methods 0.000 description 1
Abstract
The invention discloses a suspension shock absorber adopting directional rotating flow self-adaptive liquid damping. The suspension shock absorber comprises a base (1), a base membrane (2), a partition board (3), an elastomer (4) and a connecting seat (5) which are arranged from bottom to top in sequence, wherein a hydraulic cavity is defined by the base membrane (2) and the elastomer (4) and filled with a shock absorption fluid; the partition board (3) divides the hydraulic cavity into an upper cavity (6.1) and a lower cavity (6.2), and an inertial channel (3.1) for communicating the upper cavity (6.1) and the lower cavity (6.2) is formed in the partition board (3). The suspension shock absorber is characterized in that a converting mechanism for converting reciprocating vibration energy of the shock absorption fluid in the vertical direction into kinetic energy circulating in a single direction is arranged in the upper cavity (6.1). According to the suspension shock absorber adopting the directional rotating flow self-adaptive liquid damping, the cavitation phenomenon at a high-frequency section can be avoided, the service life of equipment is prolonged, the high-frequency hardening phenomenon can be eliminated, and accordingly, the shock absorption effect is good.
Description
Technical field
The present invention relates to the technical field of vibration damper, specifically a kind of directed eddy flow self adaption Hydraulic Engine Mount vibration damper.
Background technique
Suspension vibration damper is a kind of link be installed on by power assembly in frame, and for reducing vibration and the noise of power assembly generation, it is come across in automobile industry the earliest, for the installation of motor.Hydraulic mount vibration damper is then in conjunction with the one suspension vibration damper that fluid power damper mechanism develops out on the basis of rubber mounting.Its basic structure is the metal frame, rubber spring and the base that sequentially connect, and three surrounds formation inner chamber, is provided with inertia channel body inner chamber being separated into upper chamber and lower chambers in inner chamber, and inertia channel body is provided with inertia channel and decoupling zero film.The static load of rubber spring supporting motive force assembly part is relied on time static, when low frequency is dynamic, rubber spring stretches the liquid convection in drive two chambers, the friction of inertia channel is relied on to consume vibrational energy, and high frequency dynamic time, because liquid inertia causes greatly high frequency to harden, the high frequency dynamic stiffness of hydraulic mount vibration damper can be reduced by decoupling zero film in the feature that the dynamic stiffness of high band is little, slow down the degree of high frequency sclerosis.Thus dynamic stiffness is large when making this existing hydraulic mount vibration damper meet certain low frequency, the requirement that during high frequency, dynamic stiffness is little.The Master's thesis " inertia channel-decoupling zero membrane type hydraulic mount characteristic research and optimal design " of Jiangsu University Zhang Chengsong can be consulted for above-mentioned existing hydraulic mount vibration damper.
But above-mentioned hydraulic mount vibration damper will cause cavitation effect in the Rapid stretching process of high band, and cavitation effect not only can corrode component internal surface thus the working life of reduction equipment, and a large amount of bubbles that cavitation effect produces will make dither only carry out compressing and stretching for bubble due to the easy compression of gas and the characteristic easily stretched, make liquid form cutout phenomenon, this is also one of key factor causing high frequency to harden.Above-mentioned high band refers to the frequency being greater than 50HZ.
Summary of the invention
Technical problem to be solved by this invention is: provide a kind of and can avoid producing cavitation phenomenon at high band, improve service life of equipment, and can eliminate high frequency hardening phenomenon, thus make the directed eddy flow self adaption Hydraulic Engine Mount vibration damper of good damping result.
The technical solution used in the present invention is: provide a kind of directed eddy flow self adaption Hydraulic Engine Mount vibration damper, it comprises base, sequentially be arranged on the counterdie on base, elastomer and the connecting base for supporting motive force assembly from the bottom up, counterdie and elastomer surround formation one hydraulic pressure cavity, be full of damping fluid in hydraulic pressure cavity, in hydraulic pressure cavity, be provided with the switching mechanism that damping fluid double vibrations vertically can be converted to the kinetic energy along single direction turnover.Due to damping fluid generation cavitation phenomenon can be caused in double vibrations process, therefore high frequency sclerosis is easily produced, and when the kinetic energy of the turnover of vibrational energy conversion in single direction, its damping fluid is all the acceleration being subject to single direction, cavitation phenomenon can not be produced, this not only avoids the infringement of cavitation phenomenon for component, also greatly reduce high frequency hardenability simultaneously.
Demarcation strip hydraulic pressure cavity being separated into upper chamber and lower chambers is provided with in hydraulic pressure cavity, demarcation strip is provided with the inertia channel being communicated with upper chamber and lower chambers, described upper chamber and bottom chamber are provided with switching mechanism all separately, and upper chamber is identical with all veers of the damping fluid that bottom chamber drives through respective switching mechanism.Vibrational energy can be made in inertia channel to convert heat energy to vias inner walls friction by inertia channel, upper chamber and bottom chamber are equipped with the efficiency that a switching mechanism can improve hot-cast socket simultaneously, certain upper chamber can only be the similar of wing wheel structure with the switching mechanism of bottom chamber, and the size of its blade can adjust according to actual demand.
Described switching mechanism comprises wing wheel, whole blades in wing wheel are uniformly distributed along the circumference of wing wheel axis, the side of blade is vertical plane, opposite side is arc surface, and the vertical plane of arbitrary blade is relative with the arc surface of adjacent blades, one end that described wing wheel and connecting base stretch in hydraulic pressure cavity is rotatably assorted.By to be vertical plane side be in side arc surface ground blade structure, by hydromechanical design, the damping fluid of back and forth flowing can be made to be all that trend blade rotates towards arc surface side, thus to realize unidirectional turnover.
Medial axis on length of blade direction is bent to form the blade structure of arc along the horizontal plane towards the arc surface side of blade.By arranging the blade of arc, can make to stir in certain inclination angle between the tip of blade and damping fluid, preventing from producing step-down locally between the tip of blade and damping fluid and producing cavitation phenomenon.
Described wing wheel is provided with throttling plate, and throttling plate and wing wheel are integral type structure.High frequency vibrating kinetic energy on connecting base can be transmitted by throttling plate and produce pressure wave, the effect of the unidirectional turn-around flow of wing wheel trend damping fluid can be had both again simultaneously.
One end that throttling plate and connecting base stretch in hydraulic pressure cavity is rotatably assorted, and whole blades of wing wheel are uniformly distributed on the outer side wall of throttling plate along the circumference of throttling plate.
Described switching mechanism comprises to be located in hydraulic pressure cavity and hydraulic pressure cavity to be separated into the demarcation strip of upper chamber and lower chambers, demarcation strip is provided with the inertia channel being communicated with upper chamber and lower chambers, described inertia channel comprises orders about the first inclination inertia channel that damping fluid circumferentially rotates and the second inclination inertia channel ordering about the rotation of damping fluid circumference when damping fluid flows into lower chambers from upper chamber when damping fluid flows into upper chamber from lower chambers, the first one-way valve only flowing into upper chamber for damping fluid from lower chambers is provided with in first inclination inertia channel, the second one-way valve only flowing into lower chambers for damping fluid from upper chamber is provided with in second inclination inertia channel, and the direction that described first inclination inertia channel and the second inclination inertia channel order about damping fluid rotation is all consistent.By two groups of inertia channels, and each inertia channel is certain tilt angle, damping fluid can be made no matter to make still all can realize from the bottom up from top to bottom the unidirectional turnover of damping fluid, its effect played and wing wheel have similarity, can improve the conversion efficiency of the kinetic energy of vibrational energy conversion in unidirectional turnover of damping fluid further.
Be provided with heat conduction board in hydraulic pressure cavity, heat conduction board is provided with the friction through hole of some damping fluids for turnover in hydraulic pressure cavity circulation, and the hole inwall sliding friction of damping fluid and friction through hole, be provided with heat radiation rack outside described hydraulic pressure cavity, heat conduction board is connected with heat radiation rack.The damping fluid of turnover is ceaselessly rubbed by the friction through hole on heat conduction board at a high speed, kinetic energy converted to energy in heat conduction board and leave eventually through heat radiation rack, can sequentially vibrational energy conversion turnover kinetic energy, turnover kinetic energy be converted to heat energy again and finally dispel the heat like this, finally reach the effect of vibration and noise reducing.
Described base and counterdie are encircled into an airtight air cavity, and base is provided with along with counterdie vibration band chamber of taking offence sucks the Non-return air valve of outside air.By the setting of air cavity and Non-return air valve, can make air cavity in vibration processes, remain the high pressure of air cavity, thus when counterdie resets upward, by the upstroke of counterdie, pull counterdie to be converted to air cavity by damping fluid promote counterdie and drive damping fluid, therefore incompressible according to liquid, but the characteristic easily stretched, further avoid due to high frequency drawing process and cause producing bubble in damping fluid.
Demarcation strip is provided with central through bore, is provided with decoupling zero film in central through bore.The degree of high frequency sclerosis further can be slowed down by decoupling zero film.
After adopting above structure, directed eddy flow self adaption Hydraulic Engine Mount vibration damper of the present invention compared with prior art has the following advantages: first, the vibrational energy vertically of damping fluid converts the kinetic energy of the circumference rotation of damping fluid to, therefore, avoid the Tension and Compression of damping fluid and produce the problem of bubble, high-frequency process is also only that turnaround speed increases, therefore the generation of cavitation phenomenon is avoided, secondly, damping fluid has certain dynamic stiffness in vibration processes, high frequency sclerosis is easily produced at high band, but make vibrational energy convert the kinetic energy of circumference rotation to by switching mechanism, therefore the dynamic stiffness of damping fluid is little, not easily there is the situation that high frequency hardens, substantially increase the application of hydraulic mount vibration damper at high band.
Accompanying drawing explanation
Fig. 1 is the assembling exploded perspective view of directed eddy flow self adaption Hydraulic Engine Mount vibration damper of the present invention.
Fig. 2 is the close-up schematic view in " A " region in Fig. 1.
Fig. 3 is the axonometric drawing of directed eddy flow self adaption Hydraulic Engine Mount vibration damper of the present invention.
Fig. 4 is the sectional view of directed eddy flow self adaption Hydraulic Engine Mount vibration damper of the present invention.
Fig. 5 is the close-up schematic view in " B " region in Fig. 4.
Fig. 6 is the structural representation after directed eddy flow self adaption Hydraulic Engine Mount vibration damper of the present invention removes wing wheel.
Fig. 7 is the structural representation after directed eddy flow self adaption Hydraulic Engine Mount vibration damper of the present invention removes wing wheel and heat conduction board.
Fig. 8 is the structural representation of directed eddy flow self adaption Hydraulic Engine Mount vibration damper single-blade wheel state of the present invention.
Fig. 9 is the structural representation after installing throttling plate after directed eddy flow self adaption Hydraulic Engine Mount vibration damper of the present invention removes wing wheel.
Figure 10 is the operating diagram of demarcation strip of the present invention and upper strata wing wheel.
Figure 11 is the structural representation of wing wheel of the present invention.
Figure 12 is the another kind of structural representation of wing wheel of the present invention.
Figure 13 is the structural representation after wing wheel of the present invention and throttling plate are assembled.
Figure 14 is the cross section enlarged diagram of wing wheel Leaf of the present invention.
Figure 15 is the structural representation of demarcation strip part of the present invention.
Figure 16 is the stagewise cutaway view schematic diagram of " C-C " in Figure 15.
Figure 17 is the structural representation of the one-way valve in inertia channel of the present invention in opening state.
Figure 18 is the structural representation of the closed state of Figure 17.
Figure 19 is structure diagram of the present invention.
Figure 20 is energy transfer process schematic diagram of the present invention.
Wherein, 1, base, 2, counterdie, 3, demarcation strip, 3.1, inertia channel, 3.1.1, first inclination inertia channel, 3.1.2, second inclination inertia channel, 3.2, central through bore, 3.3, upper demarcation strip, 3.4, lower demarcation strip, 3.5, scaffold, 4, elastomer, 5, connecting base, 6.1, upper chamber, 6.2, lower chambers, 7, wing wheel, 7.1, blade, 7.1.1, vertical plane, 7.1.2, arc surface, 8, throttling plate, 9, coupling shaft, 10, Non-return air valve, 11, decoupling zero film, 12, heat conduction board, 12.1, friction through hole, 13, heat radiation rack, 14, bound edge, 15, air cavity.
Embodiment
Below in conjunction with the drawings and specific embodiments, the invention will be further described.
" directed eddy flow " in the present invention refers to along the turnover of hydraulic pressure cavity single direction, namely directed rotational flow." self adaption " in the present invention refers to the directed eddy flow of acceleration that switching mechanism is directly proportional along with the increase of amplitude and vibration frequency, therefore the frictional heat energy that converts to of its eddy flow is also larger, that is the heat produced along with the increase of amplitude and vibration frequency also higher, damping effect is also more obvious, can prevent the generation of hardening phenomenon, therefore this system definition is " self adaption " damped system.
As shown in the figure, the invention provides a kind of directed eddy flow self adaption Hydraulic Engine Mount vibration damper, it comprises base 1, sequentially be arranged on the counterdie 2 on base 1, elastomer 4 and the connecting base 5 for supporting motive force assembly from the bottom up, counterdie 2 and elastomer 4 surround formation one hydraulic pressure cavity, be full of damping fluid in hydraulic pressure cavity, in hydraulic pressure cavity, be provided with the switching mechanism that damping fluid double vibrations vertically can be converted to the kinetic energy along single direction turnover.
Above-mentioned elastomer 4 is quality of rubber materials, and in order to the rigidity that improves elastomer 4 and elastomer 4 and the connection sealing between connecting base 5 and demarcation strip 3, be provided with bound edge 14 outside described elastomer 4, described bound edge 14 is made with elastomer 4 integrated vulcanizing.The lower end bending of described bound edge 14 is pressed on the flange lower end surface of base 1.
The demarcation strip 3 hydraulic pressure cavity being separated into upper chamber 6.1 and lower chambers 6.2 is provided with in hydraulic pressure cavity, demarcation strip 3 is provided with the inertia channel 3.1 being communicated with upper chamber 6.1 and lower chambers 6.2, switching mechanism is provided with all separately in described upper chamber 6.1 and lower chambers 6.2, and all veers of the damping fluid driven through respective switching mechanism in upper chamber 6.1 and lower chambers 6.2 are identical, switching mechanism in described lower chambers 6.2 is connected with the switching mechanism in upper chamber 6.1 by coupling shaft 9, and demarcation strip 3 is provided with the through hole run through for coupling shaft 9.Above-mentioned demarcation strip 3, also known as making damp generator in industry.And the inertia channel 3.1 on demarcation strip 3 should be called damp channel actually, just because its channel definition is inertia channel by traditional shock absorber, the origin of so-called inertia channel is because the inertia that liquid vibrates back and forth in this passage is greatly named, and the liquid of this passage of structure of the present invention is single direction flowing, therefore the accurate definition of its title should be damp channel, but consider the understanding of those of ordinary skill in industry, still adopt inertia channel 3.1.
Described switching mechanism comprises wing wheel 7, whole blades 7.1 in wing wheel 7 are uniformly distributed along the circumference of wing wheel 7 axis, the side of blade 7.1 is vertical plane 7.1.1, opposite side is arc surface 7.1.2, and the vertical plane 7.1.1 of arbitrary blade 7.1 is relative with the arc surface 7.1.2 of adjacent blades 7.1, one end that described wing wheel 7 and connecting base 5 stretch in hydraulic pressure cavity is rotatably assorted.
Medial axis on blade 7.1 length direction is bent to form the blade structure of arc along the horizontal plane towards the arc surface 7.1.2 side of blade 7.1.As shown in Figure 9, described blade 7.1 entirety is in arc line shaped, but its object is between the end of blade 7.1 free end and damping fluid in certain inclination angle, stir between minimizing blade 7.1 free end and damping fluid and produce bubble, therefore, as long as the free end of its blade 7.1 is certain arc, convenient certainly in order to processes, is arranged to overall arc line shaped by blade.
Described wing wheel 7 is provided with throttling plate 8, and throttling plate 8 and wing wheel 7 are integral type structure.Throttling plate can transmission of pressure ripple, its can to a certain degree improvement liquid high frequency sclerosis characteristic, therefore the combination of throttling plate 8 and wing wheel 7 is passed through, can be that a vibrational energy part changes the kinetic energy in turnover by wing wheel 7, a part carries out vibration damping by throttling plate 8 mineralization pressure wave loops to decoupling zero film.
One end that throttling plate 8 and connecting base 5 stretch in hydraulic pressure cavity is rotatably assorted, and whole blades 7.1 of wing wheel 7 are uniformly distributed on the outer side wall of throttling plate 8 along the circumference of throttling plate 8.As shown in Figure 9, throttling plate 8 is located at inner side, and wing wheel 7 is located at outside, and certainly, also wing wheel 7 can be located at inner side, and throttling plate 8 is located at outside, more or by the two be connected in series vertically, these are all the conversions of the locations of structures of carrying out on this basis.
Also switching mechanism is provided with in described lower chambers 6.2, and all veers of the damping fluid driven through respective switching mechanism in upper chamber 6.1 and lower chambers 6.2 are identical, switching mechanism in described lower chambers 6.2 is connected with the switching mechanism in upper chamber 6.1 by coupling shaft 9, and demarcation strip 3 is provided with the through hole run through for coupling shaft 9.Switching mechanism in described lower chambers 6.2 can be same wing wheel 7 structure.
As improvement, wing wheel 7 rotates often to be needed to be installed by axle and bearing, in order to avoid producing resonant impact between wing wheel 7 and bearing, the ball bearing structure of two point contact can be adopted to install, and on upper and lower outer ring, add preloading spring for eliminating the collision of wing wheel 7 and bearing.Above-mentioned spring can select turriform wire spring, also can be thin-walled disc spring etc., and the object of its design is to avoid dither to make play between wing wheel 7 and bearing, and mutually collides and produce man-made further destroy.
Described switching mechanism comprises to be located in hydraulic pressure cavity and hydraulic pressure cavity to be separated into the demarcation strip 3 of upper chamber 6.1 and lower chambers 6.2, demarcation strip 3 is provided with the inertia channel 3.1 being communicated with upper chamber 6.1 and lower chambers 6.2, the definition of the same inertia channel 3.1 above of definition of described inertia channel 3.1, described inertia channel 3.1 comprises orders about the first inclination inertia channel 3.1.1 that damping fluid circumferentially rotates and the second inclination inertia channel 3.1.2 ordering about the rotation of damping fluid circumference when damping fluid flows into lower chambers 6.2 from upper chamber 6.1 when damping fluid flows into upper chamber 6.1 from lower chambers 6.2, the first one-way valve only flowing into upper chamber 6.1 for damping fluid from lower chambers 6.2 is provided with in first inclination inertia channel 3.1.1, the second one-way valve only flowing into lower chambers 6.2 for damping fluid from upper chamber 6.1 is provided with in second inclination inertia channel 3.1.2, and the direction that described first inclination inertia channel 3.1.1 and the second inclination inertia channel 3.1.2 order about damping fluid rotation is all consistent.
In addition, as shown in Figure 17 and Figure 18, as preferably, the first above-mentioned one-way valve and all each freedom at least two of the second one-way valve can the film lobe of relative folding be formed, gap between film lobe is the passage for fluid circulation, film lobe is combined to form dome-shaped structure or pyramid-shaped structures each other, and the top of dome-shaped structure or pyramid-shaped structures is towards consistent with fluid flow direction; Or above-mentioned one-way valve is that in one, ring plate and an outer ring plate are formed, outer ring plate is nested with in interior ring plate, gap between outer ring plate and interior ring plate is the passage for fluid circulation, interior ring plate and outer ring plate are combined to form the arch structure that hoop extends each other, and the top of arch structure is towards consistent with fluid flow direction.Make above-mentioned one-way valve of the present invention meet the requirement of high frequency response with this, and in prior art, can there is the situation of high frequency sclerosis inefficacy in the one-way valve of common film valve structure in high-frequency process.So the one-way valve in the present invention also may be defined as unidirectional quick-acting valve.
Certainly no matter be that wing wheel or the inertia channel be obliquely installed coordinate one-way valve, it is all independent switching mechanism, certainly, also can be combined, namely in upper chamber 6.1, wing wheel is set, and demarcation strip being arranged equally the inclination inertia channel be obliquely installed, the direction that described first inclination inertia channel 3.1.1, the second inclination inertia channel 3.1.2 and wing wheel 7 order about damping fluid rotation is all consistent.
Heat conduction board 12 is provided with in hydraulic pressure cavity, heat conduction board 12 is as shown in the figure in certain three-dimensional cavity structure, therefore also can be described as collector mat, heat conduction board 12 is provided with the friction through hole 12.1 of some damping fluids for turnover in hydraulic pressure cavity circulation, and the hole inwall sliding friction of damping fluid and friction through hole 12.1, certainly owing to being the friction between liquid and cavity inner wall, industry is for this type of sliding friction, be referred to as flowage friction again, for the ease of the understanding of those of ordinary skill, therefore only summarize with sliding friction.Be provided with heat radiation rack 13 outside described hydraulic pressure cavity, heat conduction board 12 is connected with heat radiation rack 13.Described friction through hole 12.1 refers to, heat conduction board 12 is provided with the some through hole, the axis of the circle corresponding to circular arc medial axis of through hole and the medial axis conllinear of hydraulic pressure cavity that extend along circular arc medial axis.Damping fluid rotates around the medial axis of hydraulic pressure cavity, and the axially bored line of the through hole 12.1 that rubs and all veers of damping fluid parallel, therefore the flow direction of damping fluid can not be changed, but energy in damping fluid produces with wall friction in the hole of friction through hole when flowing through in friction through hole can be.
Described base 1 surrounds an airtight air cavity 15 with counterdie is 2-in-1, and base 1 is provided with along with counterdie 2 vibration band chamber 15 of taking offence sucks the one-way valve 10 of outside air.
Demarcation strip 3 is provided with central through bore 3.2, is provided with decoupling zero film 11 in central through bore 3.2.Because demarcation strip 3 is provided with the central through bore 3.2 for installing decoupling zero film 11, therefore, in order to better install coupling shaft 9, reduce the disturbance of coupling shaft 9, therefore on demarcation strip 3, arrange scaffold, scaffold is provided with the bearing be rotatably assorted with coupling shaft 9.
The simple declaration of each symbol and effect thereof in Figure 19 and Figure 20: first hydraulic pressure cavity is distinguished with the transmittance process of vibration source, the hydraulic chamber that first vibration source acts on, be defined as No. 0 chamber, its each parameter represents with subscript 0, and this chamber effect transfers mechanical vibrational energy to hydraulic energy; Through wing wheel first time to F
iNhydraulic pressure cavity after (t) amplitude attenuation, be defined as No. 1 chamber, its parameter represents with 1 with subscript, and the Main Function of this chamber is that small size pressure after decaying acts on and is separated on dividing plate, and is guided into ' directed damp channel ' by most of pressure energy; The Main Function of its damp channel is exactly, and pressure energy is transferred to the energy of flow and forms larger retardation angle; Thereafter, this liquid flows into No. 2 chambers below dividing plate, the each parameter of this chamber represents with 2 with subscript, the Main Function of this chamber is exactly the pressure energy again energy of flow being transferred to retardation angle, and acting on cylinder body bracket, this pressure energy reacts on dividing plate again under the effect of rubber avert by prayers contraction elasticity simultaneously.This hysteresis pressure not only effectively can react on vibration source in low-frequency range, and is being greater than ω
0the radio frequency head of vibration damper natural frequency, due to retardation angle convergence pi/2, just serves the effect of " vibration isolation ".
F
iNthe function of time representation of the vibration force of (t)-input end; F
oUTthe function of time representation of the vibration force of (t)-output terminal; K
r-rubber spring elasticity coefficient; B
r-rubber spring damping constant; The net sectional area of S-fluid passage; P-liquid pressure;
-the lift angle of spiral damping passage; The quality of m-coasting body; A-inertial acceleration; μ-hydrodynamic viscosity; F
ζ(j ω)-liquid is along the complex function representation of journey damping force; H
f-the linear loss (unit: m) of flow of fluid; Volume rigidity (the unit: N/mm of C-elastomer (this example is ' decoupling zero film ')
3); The linear velocity of υ-flow of fluid; ρ-fluid density; Heat-the heat energy distributed.
' K
r-B
rsupport system '-refer to K
r, B
rthe support system of two characteristics; The existence of ' the large damped system of passage υ-μ '-passage internal cause μ is as flow of fluid υ > 0, and the system along journey damping force produced; ' υ-P converting system '-liquid stream kinetic energy is transferred to the system of hydraulic energy; ' m-a system '-finger-type becomes the system of inertial force.
So just can according to energy transfer process schematic diagram, founding mathematical models, and according to every layer of energy transferring relation, expand the evolution process of function, omit herein.In addition, also can find out from this figure: ' decoupling zero film ' is the redundant system of ' wing wheel amplitude fading damped system ', so, there is the vibration damper of wing wheel structure can not need decoupling zero membrane structure.
In addition, then to ' wing wheel ' function equivalent with ' damping hole ' being explained: see А. Я Lie Ernieer work, Liu Dingyi translate on " cybernetics basis ", input identical signal υ to black box
0(t), P
0t (), according to Bernoulli's equation: P
0+ 1/2 × ρ υ
0 2+ ρ gh
0=P
1+ 1/2 × ρ υ
1 2+ ρ gh
1, have when losing along stroke pressure, this formula is then:
P
0+1/2×ρυ
0 2+ρgh
0＝P
1+1/2×ρυ
1 2+ρgh
1+ΔP
ζ………………………(1)
Be pressure loss value Δ P in above formula
ζ,
∵
Due to Δ W
ζfor the heat energy that damp channel distributes, so Δ P
ζ=H
ζfor heat radiation power.
∴ damping hole exports as υ
1(t), P
1(t), H
ζ(t).
Equally, wing wheel rotates liquid rotating speed by υ
0rise to υ
cr, meet Bernoulli's equation equally according to principle of conservation of energy, its wing wheel is υ to No. 1 chamber input parameter
1(t), P
1(t), H
ζ(t),
So ' wing wheel amplitude fading damped system ' is similar with ' resistance channel ' system.
Its working principle is, the kinetic energy along single direction turnover is converted into by the kinetic energy of the double vibrations by damping fluid, thus avoid damping fluid and produce cavitation phenomenon due to stretching action in dither process, and the harm of cavitation phenomenon has had more scientific paper, just do not repeat at this.Simultaneously also just because of cavitation phenomenon, make to form cutout phenomenon in the middle of liquid, namely air is easily compression and easily draws high, and the bubble that therefore cavitation phenomenon produces forms air layer, and vibrational energy cannot be transmitted, and this namely produces one of reason of high frequency sclerosis.And the situation of liquid stretching obviously can not be there is when vibrational energy converts the turnover kinetic energy of single direction to, namely can not produce cavitation phenomenon.
In addition, damping fluid damping fluid in vibration processes of tradition vibration damper is in variable accelerated motion, namely the motion mode that jerking movement degree is non-vanishing, so often driven amount of liquid is not enough, therefore the conversion of vibrational energy is not high, produce shake down phenomenon thus, and in vane belt hydrodynamic body circular flow, when vibration frequency is constant, the rotation process of its damping fluid is permanent accelerated motion, namely jerking movement degree is zero, therefore also just decreases the generation of high frequency sclerosis.
Claims (10)
1. a directed eddy flow self adaption Hydraulic Engine Mount vibration damper, it comprises the base (1) sequentially arranged from the bottom up, counterdie (2), demarcation strip (3), elastomer (4) and the connecting base (5) for supporting motive force assembly, counterdie (2) and elastomer (4) surround formation one hydraulic pressure cavity, damping fluid is full of in hydraulic pressure cavity, hydraulic pressure cavity is separated into upper chamber (6.1) and lower chambers (6.2) by demarcation strip (3), and demarcation strip (3) is provided with the inertia channel (3.1) being communicated with upper chamber (6.1) and lower chambers (6.2), it is characterized in that: in upper chamber (6.1), be provided with the switching mechanism that damping fluid double vibrations vertically can be converted to the kinetic energy along single direction turnover.
2. directed eddy flow self adaption Hydraulic Engine Mount vibration damper according to claim 1, it is characterized in that: described switching mechanism comprises wing wheel (7), whole blades (7.1) in wing wheel (7) are uniformly distributed along the circumference of wing wheel (7) axis, the side of blade (7.1) is vertical plane (7.1.1), opposite side is arc surface (7.1.2), and the vertical plane (7.1.1) of arbitrary blade (7.1) is relative with the arc surface (7.1.2) of adjacent blades (7.1), one end that described wing wheel (7) and connecting base (5) stretch in hydraulic pressure cavity is rotatably assorted.
3. directed eddy flow self adaption Hydraulic Engine Mount vibration damper according to claim 2, is characterized in that: the medial axis on blade (7.1) length direction is bent to form the blade structure of arc along the horizontal plane towards the arc surface of blade (7.1) (7.1.2) side.
4. directed eddy flow self adaption Hydraulic Engine Mount vibration damper according to claim 2, is characterized in that: described wing wheel (7) is provided with throttling plate (8), and throttling plate (8) and wing wheel (7) are integral type structure.
5. directed eddy flow self adaption Hydraulic Engine Mount vibration damper according to claim 4, it is characterized in that: one end that throttling plate (8) and connecting base (5) stretch in hydraulic pressure cavity is rotatably assorted, whole blades (7.1) of wing wheel (7) are uniformly distributed on the outer side wall of throttling plate (8) along the circumference of throttling plate (8).
6. directed eddy flow self adaption Hydraulic Engine Mount vibration damper according to claim 1, it is characterized in that: described lower chambers is also provided with switching mechanism in (6.2), and all veers of the damping fluid driven through respective switching mechanism in upper chamber (6.1) and lower chambers (6.2) are identical, switching mechanism in described lower chambers (6.2) is connected with the switching mechanism in upper chamber (6.1) by coupling shaft (9), and demarcation strip (3) is provided with the through hole run through for coupling shaft (9).
7. directed eddy flow self adaption Hydraulic Engine Mount vibration damper according to claim 1, it is characterized in that: described inertia channel (3.1) comprises orders about the first inertia channel (3.1.1) that damping fluid circumferentially rotates and the second inertia channel (3.1.2) ordering about the rotation of damping fluid circumference when damping fluid flows into lower chambers (6.2) from upper chamber (6.1) when damping fluid flows into upper chamber (6.1) from lower chambers (6.2), be provided with in first inertia channel (3.1.1) and only supply damping fluid to flow into the first one-way valve of upper chamber (6.1) from lower chambers (6.2), be provided with in second inertia channel (3.1.2) and only supply damping fluid to flow into the second one-way valve of lower chambers (6.2) from upper chamber (6.1), and described first inertia channel (3.1.1), the direction that damping fluid rotation is ordered about in second inertia channel (3.1.2) and switching mechanism is all consistent.
8. directed eddy flow self adaption Hydraulic Engine Mount vibration damper according to claim 1, it is characterized in that: in hydraulic pressure cavity, be provided with heat conduction board (12), heat conduction board (12) is provided with the friction through hole (12.1) of some damping fluids for turnover in hydraulic pressure cavity circulation, the hole inwall sliding friction of damping fluid and friction through hole (12.1), be provided with heat radiation rack (13) outside described hydraulic pressure cavity, heat conduction board (12) is connected with heat radiation rack (13).
9. directed eddy flow self adaption Hydraulic Engine Mount vibration damper according to claim 1, it is characterized in that: described base (1) and counterdie (2) are encircled into an airtight air cavity (15), base (1) is provided with along with counterdie (2) vibration band chamber (15) of taking offence sucks the Non-return air valve (10) of outside air.
10. directed eddy flow self adaption Hydraulic Engine Mount vibration damper according to claim 1, is characterized in that: demarcation strip (3) is provided with central through bore (3.2), is provided with decoupling zero film (11) in central through bore (3.2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510578123.8A CN105202096B (en) | 2015-09-11 | 2015-09-11 | Orientation eddy flow self adaptation Hydraulic Engine Mount shock absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510578123.8A CN105202096B (en) | 2015-09-11 | 2015-09-11 | Orientation eddy flow self adaptation Hydraulic Engine Mount shock absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105202096A true CN105202096A (en) | 2015-12-30 |
| CN105202096B CN105202096B (en) | 2017-06-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510578123.8A Expired - Fee Related CN105202096B (en) | 2015-09-11 | 2015-09-11 | Orientation eddy flow self adaptation Hydraulic Engine Mount shock absorber |
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| Country | Link |
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| CN (1) | CN105202096B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0914336A (en) * | 1995-06-27 | 1997-01-14 | Nok Megurasutikku Kk | Liquid filling type mount |
| RU2229636C1 (en) * | 2002-08-29 | 2004-05-27 | Образцов Дмитрий Иванович | Hydraulic support for automobile power unit suspension |
| CN2849316Y (en) * | 2005-09-08 | 2006-12-20 | 吉林大学 | Active controlled engine hydraulic pendant |
| CN201615173U (en) * | 2009-11-16 | 2010-10-27 | 浙江吉利汽车研究院有限公司 | Engine hydraulic left suspension |
| CN102829127A (en) * | 2012-09-20 | 2012-12-19 | 重庆大学 | Magneto-rheological damper of automobile engine suspension system |
| CN203335718U (en) * | 2013-05-17 | 2013-12-11 | 宁波市明诚汽车部件有限公司 | Engine hydraulic mounting mechanism provided with flow blocking block |
-
2015
- 2015-09-11 CN CN201510578123.8A patent/CN105202096B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0914336A (en) * | 1995-06-27 | 1997-01-14 | Nok Megurasutikku Kk | Liquid filling type mount |
| RU2229636C1 (en) * | 2002-08-29 | 2004-05-27 | Образцов Дмитрий Иванович | Hydraulic support for automobile power unit suspension |
| CN2849316Y (en) * | 2005-09-08 | 2006-12-20 | 吉林大学 | Active controlled engine hydraulic pendant |
| CN201615173U (en) * | 2009-11-16 | 2010-10-27 | 浙江吉利汽车研究院有限公司 | Engine hydraulic left suspension |
| CN102829127A (en) * | 2012-09-20 | 2012-12-19 | 重庆大学 | Magneto-rheological damper of automobile engine suspension system |
| CN203335718U (en) * | 2013-05-17 | 2013-12-11 | 宁波市明诚汽车部件有限公司 | Engine hydraulic mounting mechanism provided with flow blocking block |
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| Publication number | Publication date |
|---|---|
| CN105202096B (en) | 2017-06-13 |
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