CN103148147B - Design method for rebound valve plate thickness of hydraulic oscillating damper - Google Patents
Design method for rebound valve plate thickness of hydraulic oscillating damper Download PDFInfo
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Abstract
The invention relates to a design method for rebound valve plate thickness of a hydraulic oscillating damper, which belongs to the technical field of oscillating dampers. The design method is characterized by comprising the following steps: a. determining the optimal design speed point and corresponding oscillating damper damping force of the thickness of a rebound valve plate; b. determining throttling pressure and flow of piston gaps; c. determining flow of a piston hole; d. determining the equivalent length of the piston hole; e. determining the throttling pressure of the piston hole; f. determining the pressure borne by the rebound valve plate at the optimal design speed point; g. determining the pressure borne by the rebound valve plate at the initial valve opening; and h. determining the design thickness h of the rebound valve plate, actual thickness of stacked valve plates hi, and plate number ni. The method can conduct optimal design of the speed point, and accurate design of the rebound valve plate thickness of the oscillating damper according to the oil line of initial valve opening of the rebound valve. Therefore, by utilizing the design method, a reliable design value of the rebound valve plate thickness can be obtained, repeated testing and modification are avoided, design and test expenses are reduced, and the development speed of the oscillating damper is accelerated.
Description
Technical Field
The invention relates to a hydraulic damper, in particular to a method for designing the thickness of a rebound valve plate of the hydraulic damper.
Background
The damping characteristic of the hydraulic shock absorber is mainly determined by parameters of a shock absorber recovery valve and a compression valve, wherein the thickness of a valve plate has important influence on the characteristic of the shock absorber, the damping matching of a suspension system and the running smoothness of a vehicle. At present, no accurate and reliable design method exists for the thickness design of the valve plate of the barrel type hydraulic damper abroad, the valve plate thickness value is determined firstly by experience, and then design parameters are finally determined by repeated tests, verification and modification methods, the main reason is that a reliable damper design technology is lacked, an accurate valve plate deformation analysis calculation formula for the thickness design of the valve plate is not given for the hydraulic damper, an accurate and reliable design method is lacked, and an accurate throttle valve plate thickness design mathematical model is difficult to establish, so that the modern CAD design of the hydraulic damper is not realized at present. China makes a breakthrough in the design aspect of hydraulic damper throttle valve parameters, for example, Shandong university of science and technology has solved the valve plate deformation analytical calculation problem, and has established a damper valve plate thickness curve fitting optimization design method, can obtain reliable valve plate thickness design values, and the damper characteristic test values are close to the characteristic design requirement values, but because the design method needs to establish valve plate thickness optimization objective functions, and needs to carry out optimization design and calculation through programming, it is difficult for common damper designers to master. With the rapid development of the automobile industry and the continuous improvement of the vehicle running speed, higher requirements are put forward on the design of the shock absorber, so a simple, accurate and reliable method for designing the thickness of the throttle plate of the hydraulic shock absorber must be established to meet the requirements on the rapid and accurate design of the hydraulic shock absorber.
Disclosure of Invention
Aiming at the defects in the prior art, the technical problem to be solved by the invention is to provide a simple, accurate and reliable method for designing the thickness of the rebound valve plate of the hydraulic shock absorber, and the design flow is shown in fig. 1.
In order to solve the technical problems, the technical scheme of the design method for the thickness of the rebound valve plate of the hydraulic shock absorber comprises the following implementation steps:
(1) determining the optimal design speed point of the thickness of the rebound valve plate And corresponding damping force of shock absorber:
Determining the optimal design speed point of the thickness of the rebound valve plate according to the rebound stroke speed characteristic curve required by the design of the shock absorberAnd corresponding damping force of shock absorberRespectively as follows:
；
；
(2) determining piston gap throttle pressureAnd flow rate:
According to step (1)Annular area between piston cylinder and piston rodDetermining at the optimum design speedPiston gap pressure at pointComprises the following steps:
；
in the formula,the inner diameter of a cylinder barrel of the piston of the shock absorber;is the diameter of the piston rod;
according to the structural parameters of the shock absorber and the oil parameters: inner diameter of piston cylinderMean piston clearanceEccentricity ofDynamic viscosity of oilLength of piston gapAnd piston gap pressureDetermining at the optimum design speedPiston gap flow at pointMeasurement ofComprises the following steps:
；
(3) determining flow rate of piston bore:
According to the oil circuit diagram after the valve is opened of the recovery valve, the following results are obtained: the piston hole is connected with the piston gap in parallel and passes through the annular area between the piston cylinder barrel and the piston rodIn step (1)And in step (2)Determining the flow through the piston boreComprises the following steps:
；
(4) determining the equivalent length of the piston bore:
According to the structure diagrams of the shock absorber piston and the rebound valve body, the local throttling loss of the shock absorber rebound valve is superposed and converted into the on-way resistance loss of oil flowing through the piston hole, and the optimal setting is determinedSpeed meterPiston bore equivalent length at pointComprises the following steps:
；
in the formula,is the physical length of the piston bore;piston bore diameter;for the speed of movement of the damperVAt the design speed pointThe coefficient of loss along the way through the piston bore,，the kinematic viscosity of the oil is shown;the local resistance coefficient of the sudden reduction of the piston elongated hole;the local coefficient of resistance for the sudden expansion of the piston bore,，is the total area of the piston bore,，，the radius of a base for fixing the rebound valve plate is arranged in the inner cavity of the rebound valve,the radius of an inner cavity of the valve is recovered, namely the radius of a valve port;the local resistance coefficient of the oil liquid flowing through the piston hole due to the change of the flow direction is obtained;
(5) determining throttle pressure of piston bore:
According to the dynamic viscosity of oilNumber of piston holesDiameter of piston boreIn step (3)And in step (4)Determining at the optimum design speedThrottle pressure of piston bore at pointComprises the following steps:
；
(6) determining the pressure of the reset valve plate at the optimum design speed:
Determining the optimum design speed according to the relationship between the piston gap pressure and the piston hole, the normal through hole and the throttle gap pressure after the valve is opened by the recovery valvePressure applied to restoring valve plate at pointComprises the following steps:
；
(7) determining the pressure to which the reset valve plate is subjected during initial opening:
According to the initial valve opening speed point of the shock absorberAnd first timeDamping force of opening valveAnd (5) repeating the step (2) to the step (6) to determine the pressure borne by the reset valve plate during the initial valve openingComprises the following steps:
；
in the formula,the throttle pressure of the piston gap at the initial valve opening,；the throttle pressure of the piston bore at the time of initial opening of the valve,，the piston hole equivalent length at the time of initial valve opening determined in step (4),for the piston bore flow rate at the initial valve opening,，the piston gap flow rate at the time of initial valve opening,；
(8) determining a design thickness of a rebound valvehAnd the thickness of the actual superposed valve sheeth i Number of sheetsn i :
According to the area of the common through hole of the recovery valveAnnular area between piston cylinder and piston rodOptimum design speedPoint and corresponding piston gap flowRestoring the pressure to which the valve plate is subjectedPressure of the return valve plate during initial openingOuter radius of rebound valver bRadius of valve port positionr kDynamic viscosity of oilDetermining the design value of the thickness of the rebound valve platehComprises the following steps:
；
wherein,，，the deformation coefficient of the rebound valve plate at the position of the valve port;
according to the design value of the thickness of the rebound valve platehAnd valve plate standard thickness series, using the equivalent thickness calculation formula of the superposed valve plate to design the thickness of the single-plate restored valve platehEquivalently splitting into superposed valve plates (，， ) The thickness and number of the recovered superposed valve plates should satisfy the equivalent thicknessEqual to the design thicknessI.e. by。
Compared with the prior art, the invention has the advantages that:
the thickness of the rebound valve plate of the hydraulic shock absorber adopts an analytic design method, utilizes a deformation analytic calculation formula under the non-uniform pressure of the valve plate and an oil nonlinear throttling loss subsection analytic calculation formula, and superposes and converts the local throttling loss into the equivalent length of a piston hole, according to the oil circuit after the first valve opening of the rebound valve, by utilizing the optimal design speed of the valve plate thickness and through the relationship among the speed, the flow rate, the throttling pressure and the valve plate deformation of the shock absorber, the thickness of the rebound valve plate of the hydraulic shock absorber is accurately modeled and designed, the thickness and the number of the rebound valve plates of the shock absorber are actually designed according to the equivalent thickness calculation formula of the rebound valve plates, the design value of the thickness of the rebound valve plates of the shock absorber is accurate and reliable, repeated tests, verification and modification are avoided, therefore, the design and test cost of the shock absorber is reduced, the development period is shortened, and the requirements of quick and accurate design of the hydraulic shock absorber can be met.
For a better understanding of the invention, reference is made to the following further description taken in conjunction with the accompanying drawings.
FIG. 1 is a flow chart of a design of the thickness of a damper rebound valve plate;
FIG. 2 is a schematic diagram of a shock absorber piston assembly and rebound valve;
fig. 3 is an oil passage diagram after the shock absorber restoring valve is opened for the first time;
FIG. 4 is a desired speed profile for the shock absorber design of the first embodiment;
FIG. 5 is a velocity profile obtained from a test of the characteristics of the design damper of the first embodiment;
FIG. 6 is a desired speed profile for the shock absorber design of embodiment two;
figure 7 is a plot of the desired speed characteristics for the design of the shock absorber of the second embodiment.
Detailed description of the preferred embodiments
The present invention will be described in further detail by way of examples.
Example one: a piston assembly and a rebound valve structure of a certain shock absorber are shown in figure 2, and comprise a piston body 1, a piston rod 2, a piston hole 3, a rebound valve plate 4, a limit retainer ring 5 and a fastening nut 6, wherein the rebound valve is opened too much to prevent the shock absorber from moving too fastWhen the shock absorber breaks down, a limit check ring 5 is arranged below the reset valve plate 4 and is fixed by a fastening nut 6; meanwhile, in order to prolong the service life of the shock absorber and prevent the shock absorber from being opened frequently when the shock absorber runs on a common road surface, the recovery valve is provided with a normally through hole 6. The structural parameters of the shock absorber, the valve body structure and the oil parameters are as follows: inner diameter of piston cylinderDiameter of piston rodd g20mm, the annular area between the piston cylinder and the piston rod(ii) a Piston gap length(ii) a Mean piston clearance(ii) a Eccentricity ratio(ii) a Kinematic viscosity of oil＝m2S, densityDynamic viscosity(ii) a Piston bore diameterNumber ofAngle of direction(ii) a Outer radius of throttle valveRadius of throttle valve portInner diameter of(ii) a Area of normal through holeNormal through hole flow coefficient(ii) a Deformation coefficient of valve plate deformation at valve port radius positionm6N; the speed profile required for the shock absorber design is shown in FIG. 4, where the shock absorber rebound valve first opening speedDamping force of first opening valve(ii) a Maximum valve opening speedMaximum opening damping force。
The thickness analytic design method for the throttle plate of the hydraulic damper provided by the embodiment of the invention comprises the following specific steps as shown in figure 1:
(1) determining the optimal design speed point of the thickness of the rebound valve plateAnd corresponding damping force of shock absorber：
According to the rebound stroke speed characteristic required by the design of the shock absorber: initial valve opening speedDamping force of first opening valve(ii) a Maximum valve opening speedMaximum opening damping forceDetermining the optimal design speed point of the thickness of the rebound valve plateAnd corresponding damping force of shock absorberRespectively as follows:
；
；
(2) determining piston gap throttle pressureAnd flow rate：
According to step (1)Annular area between piston cylinder and piston rodDetermining at the optimum design speedPiston gap throttle pressure at pointComprises the following steps:
；
according to the structural parameters of the shock absorber and the oil parameters: inner diameter of piston cylinderMean piston clearanceEccentricity ofDynamic viscosity of oilLength of piston gapAnd piston gap pressureDetermining at the optimum design speedPiston gap flow at pointComprises the following steps:
；
(3) determining flow rate of piston bore ：
According to the oil path diagram 3 after the recovery valve is opened, the annular area between the piston cylinder and the piston rodIn step (1)And in step (2)Determining the flow through the piston boreIs composed of
；
(4) Determining the equivalent length of the piston bore：
Thus, it is possible to provideAccording to the physical length of the piston bore(ii) a Piston bore diameterCoefficient of local pressure loss、、And coefficient of piston bore on-way pressure lossDetermining the optimum design speed of the piston boreEquivalent length at pointComprises the following steps:
；
in the formula,＝0.025，， ，＝m2/s；the local resistance coefficient for the sudden reduction of the piston slender hole can be obtained by looking up the table；The local coefficient of resistance for the sudden expansion of the piston bore,，， ， ，，；the local resistance coefficient of the oil flowing through the piston hole due to the change of the direction, ，；
(5) determining throttle pressure of piston bore：
According to the dynamic viscosity of oilDiameter of piston boreNumber ofIn step (3)And in step (4)Determining at the optimum design speed DotThrottle pressure of piston boreComprises the following steps:
；
(6) determining the pressure of the reset valve plate at the optimum design speed：
Fig. 3 shows the oil passage after the valve is opened: the pressure applied on the reset valve plate is equal to the throttling pressure of the constant through hole. According to step (2)And in step (6)Determining at the optimum design speedPressure applied to the valve plate at the time of point-time restoration：
；
(7) Determining the pressure on the valve plate when the valve is opened for the first time：
According to the initial valve opening speed pointAnd the damping force of the shock absorber required at that pointAnd (6) repeating the step (2) to the step (6), and determining the pressure applied to the reset valve sheet when the valve is opened for the first timeComprises the following steps:
；
in the formula,the piston gap throttle pressure when the valve is opened for the first time,；for the throttling pressure of the piston bore at the time of initial valve opening，Piston bore equivalent length at first valve opening，For the piston bore flow at the time of initial valve opening，Is the piston gap flow at the time of initial valve opening；
(8) Determining a design thickness of a rebound valvehAnd the thickness of the actual superposed valve sheeth i Number of sheetsn i ：
Restoring the area of the valve through hole according to the oil circuit diagram after the initial valve openingAnnular area between piston cylinder and piston rodOptimum design speedPoint and corresponding piston gap flowRestoring the pressure to which the valve plate is subjectedPressure of the return valve plate during initial openingRestoring the outer radius of the throttle valveRadius of valve port positionCoefficient of deformation of rebound valve at valve port radiusm6Determining the designed value of the thickness of the rebound valve platehComprises the following steps:
；
wherein,，；
according to the design value of the thickness of the rebound valve platehAnd valve plate standard thickness series, using the equivalent thickness calculation formula of the superposed valve plate to design the thickness of the single-plate restored valve platehEquivalently splitting into superposed valve plates (，， ) The thickness and number of the recovered superposed valve plates should satisfy the equivalent thicknessEqual to the design thicknessI.e. byAnd the thickness and the number of the superposed valve plates are obtained as follows:
；；；
the equivalent thickness of the actual recovery sandwich valve sheet is ＝0.286mm。
The comprehensive performance test bed of the electrohydraulic servo shock absorber is utilized to carry out characteristic test on a shock absorber prototype which is designed and processed, the measured speed characteristic curve of the shock absorber is shown in figure 5, and the result shows that the design value of the thickness of the throttle valve plate of the hydraulic shock absorber is reliable, and the design method of the thickness of the throttle valve plate of the tubular hydraulic shock absorber is correct.
Example two: the return speed characteristic required for a certain hydraulic shock absorber design is, as shown in FIG. 6, the initial valve opening speedDamping force of first opening valve(ii) a Maximum valve opening speedMaximum opening damping forceThe structural parameters and the oil parameters of the shock absorber are the same as those of the first embodiment.
By adopting the design steps of the first embodiment, the thickness of the rebound valve plate of the shock absorber is designed, and the obtained design value of the thickness of the rebound valve plateh＝0.267mm2(ii) a The thickness and the number of the actual rebound valve plates of the shock absorber are respectively as follows:
；；；
the equivalent thickness of the actual recovery sandwich valve sheet is ＝0.2674mm。
The comprehensive performance test bed of the electrohydraulic servo shock absorber is utilized to carry out characteristic test on a shock absorber prototype which is designed and processed, the measured speed characteristic curve of the shock absorber is shown in figure 7, and the result shows that the design value of the thickness of the throttle valve plate of the hydraulic shock absorber is reliable, and the design method of the thickness of the throttle valve plate of the tubular hydraulic shock absorber is correct.
EXAMPLE III: the designed restoring speed characteristic curve of a certain hydraulic shock absorber is the same as that of the embodiment; shock absorber with piston rod diameterd gExcept 18mm, other structural parameters and oil parameters are identical to those of the first example.
By adopting the design steps of the first embodiment, the thickness of the rebound valve plate of the shock absorber is designed, and the obtained design value of the thickness of the rebound valve plateh＝0.243mm2(ii) a The thickness and the number of the actual recovery superposed valve plates are respectively as follows:
；；；
the equivalent thickness of the actual recovery sandwich valve sheet is ＝0.2431mm。
Claims (1)
1. The method for designing the thickness of the rebound valve plate of the hydraulic shock absorber comprises the following specific steps:
(1) determining the optimal design speed point V of the thickness of the rebound valve platehoAnd corresponding damping force F of shock absorberdho:
Determining an optimal design speed point V of the thickness of the rebound valve plate according to a rebound stroke speed characteristic curve required by the design of the shock absorberhoAnd corresponding damping force F of shock absorberdhoRespectively as follows:
Vho＝Vk1+0.618(Vk2-Vk1)；
(2) determining piston gap throttle pressure pHoSum flow rate QHo:
According to F in step (1)dhoAnnular area between piston cylinder and piston rodIs determined at the optimum design speed VhoPiston gap pressure p at pointHoComprises the following steps:
pHo＝Fdho/SH；
in the formula, DHThe inner diameter of a cylinder barrel of the piston of the shock absorber; dgIs the diameter of the piston rod;
according to the structural parameters of the shock absorber and the oil parameters: inner diameter D of piston cylinderHPiston meanGap deltaHEccentricity e, hydrodynamic viscosity μ of the oiltLength of piston gap LHAnd piston gap pressure pHoDetermining at the optimum design speed VhoPiston gap flow Q at pointHoComprises the following steps:
(3) determining the flow rate Q of a piston boreho:
According to the oil circuit diagram after the valve is opened of the recovery valve, the following results are obtained: the piston hole is connected with the piston gap in parallel and passes through the annular area S between the piston cylinder and the piston rodHV in step (1)hoAnd Q in step (2)HoDetermining the flow rate Q through the piston borehoComprises the following steps:
Qho＝VhoSH-QHo；
(4) determining the equivalent length L of the piston boreheo:
According to the structure diagrams of the shock absorber piston and the rebound valve body, the local throttling loss of the shock absorber rebound valve is superposed and converted into the on-way resistance loss of oil flowing through the piston hole, and the optimal design speed V is determinedhoPiston bore equivalent length at point LheoComprises the following steps:
in the formula, LhIs the physical length of the piston bore; dhPiston bore diameter; lambda [ alpha ]hFor the damper movement velocity V at the design velocity point VhoThe coefficient of loss along the way through the piston bore,v is the kinematic viscosity of the oil liquid; zetah1The local resistance coefficient of the sudden reduction of the piston elongated hole; zetah2Local coefficient of resistance, ζ, for sudden enlargement of the piston boreh2＝[1-Ah/SF]2，AhIs the total area of the piston bore,raradius r for mounting and fixing base of rebound valve sheet in inner cavity of rebound valvekThe radius of an inner cavity of the valve is recovered, namely the radius of a valve port; zetah3The local resistance coefficient of the oil liquid flowing through the piston hole due to the change of the flow direction is obtained;
(5) determining the throttle pressure p of a piston boreho:
According to the dynamic viscosity mu of the oiltNumber n of piston boreshDiameter d of piston borehQ in step (3)hoAnd L in step (4)heoDetermining at the optimum design speed VhoThrottle pressure p of the piston bore at the time of ignitionhoComprises the following steps:
(6) determining the pressure p borne by the reset valve plate at the optimal design speedfo:
Determining the optimal design speed V according to the relationship between the piston gap pressure and the piston hole, the normal through hole and the throttle gap pressure after the recovery valve is openedhoPressure p on restoring valve plate at pointfoComprises the following steps:
pfo＝pHo-pho；
(7) determining the pressure p to which the reset valve plate is subjected during initial openingfk1:
According to the primary valve opening speed point V of the shock absorberk1And first opening damping force Fdk1And (5) repeating the steps (2) to (6) to determine the pressure p borne by the reset valve plate when the valve is opened for the first timefk1Comprises the following steps:
pfk1＝pHk1-phk1；
in the formula, pHk1For throttling pressure of piston gap at initial opening，pHk1＝Fdk1/SH；phk1The throttle pressure of the piston bore at the time of initial opening of the valve,Lhek1the piston hole equivalent length in the initial valve opening, Q, obtained in step (4)hk1For the piston bore flow at the time of initial valve opening, Qhk1＝Vk1SH-QHk1，QHk1The piston gap flow rate at the time of initial valve opening, <math>
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(8) determining the design thickness h of the rebound valve plate and the thickness h of the actual superposition valve plateiAnd the number n of sheetsi:
According to the area A of the common through hole of the recovery valve0Annular area S between piston cylinder and piston rodHOptimum design velocity VhoPoint and corresponding piston gap flow QHoRestoring the pressure p to which the valve plate is subjectedfoRestoring valve platePressure p applied during initial openingfk1Outer radius r of rebound valvebRadius of valve port position rkDynamic viscosity of oil mutDetermining the design value h of the thickness of the rebound valve plate as follows:
wherein, <math>
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</math> Grkthe deformation coefficient of the rebound valve plate at the position of the valve port;
according to the design value h of the thickness of the rebound valve plate and the standard thickness series of the valve plate, the design thickness h of the single rebound valve plate is equivalently split into the rebound valve plate (h) by using a calculation formula of the equivalent thickness of the rebound valve plate1，n1，h2，n2，…hn，nn) The thickness and the number of the recovery superposed valve plates should satisfy the equivalent thickness heEqual to the design thickness h, i.e.
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| US6837344B2 (en) * | 2001-02-12 | 2005-01-04 | Delphi Technologies, Inc. | Piston and rod assembly for air-actuated variable damping |
| JP2004003562A (en) * | 2002-05-31 | 2004-01-08 | Mitsubishi Motors Corp | Shock absorber |
| DE10351357B3 (en) * | 2003-11-04 | 2005-02-24 | Zf Friedrichshafen Ag | Fluid resistance valve for use in vibration damper has valve flaps pushed down onto plate with holes or parallel against Belleville washer to allow flow of fluid through holes |
| CN2797772Y (en) * | 2005-05-20 | 2006-07-19 | 万向钱潮股份有限公司 | Compression valve for vehicle shock absorber |
| DE102008042103A1 (en) * | 2008-09-15 | 2010-03-25 | Zf Friedrichshafen Ag | Vibration damper with amplitude-selective damping force |
| CN102840265B (en) * | 2012-07-18 | 2014-07-23 | 山东理工大学 | Optimal design method for parameter of controllable cylinder type hydraulic buffer of semi-active suspension |
-
2013
- 2013-03-08 CN CN201310073563.9A patent/CN103148147B/en not_active Expired - Fee Related
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