CN102840265A - Optimal design method for parameter of controllable cylinder type hydraulic buffer of semi-active suspension - Google Patents

Optimal design method for parameter of controllable cylinder type hydraulic buffer of semi-active suspension Download PDF

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Publication number
CN102840265A
CN102840265A CN2012103577685A CN201210357768A CN102840265A CN 102840265 A CN102840265 A CN 102840265A CN 2012103577685 A CN2012103577685 A CN 2012103577685A CN 201210357768 A CN201210357768 A CN 201210357768A CN 102840265 A CN102840265 A CN 102840265A
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China
Prior art keywords
throttle
valve
vibration damper
hole
damping
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CN2012103577685A
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Chinese (zh)
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CN102840265B (en
Inventor
周长城
赵雷雷
毛少坊
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山东理工大学
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Priority to CN201210357768.5A priority patent/CN102840265B/en
Publication of CN102840265A publication Critical patent/CN102840265A/en
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Abstract

The invention relates to an optimal design method for a parameter of a controllable cylinder type hydraulic buffer of a semi-active suspension. The optimal design method is characterized by adopting the following steps: 1), determining the damping ratio of a vehicular suspension system; 2), designing an open valve damping coefficient of a buffer speed property recover route; 3), determining the damping force of the reducer at a golden cutting speed point; 4), determining the design area of an adjustable damping hole of the reducer; 5), repeating the steps 2) to 4), calculating the adjustable damping hole area required by the thickness of the design valve block is calculated; repeating the steps 2) to 4) again, and calculating the minimum area of the adjustable damping hole; 6), determining the throttle seam pressure when a controllable valve of the buffer is opened at the first time; 7), determining the throttle seam pressure and the piston hole flow rate at the thickness designed speed point of the controllable valve throttle valve block; 8), determining the design thickness of the controllable valve throttle valve block. By adopting the design method, the design value of the valve parameter is exact and reliable; the repeatedly test and modification are avoided; the design cost of the controllable buffer is reduced; and the development cycle of the buffer is shortened.

Description

The controlled cylinder type hydraulic shock absorber valve of semi-active suspension optimum Design of Parameters method
Technical field
The present invention relates to automotive semi-active suspension, particularly the design method of the controlled cylinder type hydraulic vibration damper of semi-active suspension controlled valve parameter.
Background technique
What the application of automotive semi-active suspension controllable damper was maximum is controlled cylinder type hydraulic vibration damper, and its damping characteristic mainly is to be determined by the shock absorber valve parameter.At present; The home and abroad is to inaccurate, the reliable design method of controlled cylinder type hydraulic shock absorber valve parameter designing; Mostly be to utilize the method for " repetition test+modification " to determine design parameter, its main cause is a home and abroad present short of reliable vibration damper designing technique.Although the existing scholar of China has carried out big quantity research to this; But still be not used in the accurate Calculation analytic expression of valve block design for controlled cylinder type hydraulic shock absorber valve parameter; Lack accurate, reliable design method; Lack the mathematical model that is used for shock absorber valve parameter precise design, seriously restricted controlled cylinder type hydraulic shock absorber valve optimum Design of Parameters, this does not conform to current motor trend.Therefore, must set up the controlled cylinder type hydraulic vibration damper of semi-active suspension controlled valve method for optimally designing parameters, to satisfy the controlled cylinder type hydraulic vibration damper of automobile fast and the requirement of precise design.
Summary of the invention
To the defective that exists in the above-mentioned existing technology, technical problem to be solved by this invention provides the controlled cylinder type hydraulic vibration damper of a kind of semi-active suspension controlled valve method for optimally designing parameters.The structure of controlled valve is as shown in Figure 1, and wherein, 1 is piston rod, and 2 is spool, and 3 is the adjustable damping hole, and 4 is piston, and 5 is the controlled valve throttle valve plate, and 6 is piston hole, and 7 is the piston rod hole.
In order to solve the problems of the technologies described above, the controlled cylinder type hydraulic vibration damper of semi-active suspension provided by the present invention controlled valve method for optimally designing parameters, the step that its technological scheme is implemented is following:
(1) confirms the vehicle suspension system damping ratio
Sprung weight according to vehicle suspension system m 2, unsprung weight m 1, bearing spring rigidity KAnd tire stiffness K t, confirm suspension system travelling comfort optimum damping ratio , the Security optimum damping ratio , suspension system is optimized damping ratio ξ Op= ξ Oc+ 0.382 ( ξ Os- ξ Oc), wherein, r k= K t/ K, r m= m 2/ m 1
(2) order ξ= ξ Oc, what design vibration damper speed characteristics were restored stroke opens the valve damping constant
According to the suspension system sprung weight m 2, suspension rate K, vibration damper installs lever ratio i, the vibration damper established angle θ, what design vibration damper speed characteristics were restored stroke opens the valve damping constant
(3) confirm the damping force of vibration damper when the golden section speed point
Open the valve damping constant according to what the vibration damper speed characteristics were restored stroke C k1 And golden section speed point V Gs=0.618 C k1 , confirm the damping force of vibration damper when the golden section speed point F Gs= C k1 V Gs
(4) confirm the design area in vibration damper adjustable damping hole
According to the annulus area between piston bore and the piston rod S r, cylinder bore D H, the piston gap length L H, the piston mean gap , eccentricity e, fluid density ρ,The fluid kinetic viscosity μ t, the piston hole number n h, the piston hole diameter d h, the piston hole equivalent length L He, the normal open throttle hole area A 0, normal open orifice flow coefficient ε 0, the adjustable damping orifice-metering coefficient ε v, piston rod hole equivalent length L Ge, the piston rod bore dia d gReach the damping force of vibration damper when the golden section speed point F Gs, confirm the design area in vibration damper adjustable damping hole
Wherein, ; ; , ;
(5) order ξ= ξ Op, repeating step (2) ~ (4), needed adjustable damping hole area when calculating the throttle slice thickness design A VhOrder again ξ= ξ Os, adjustable damping Kongzui small size is calculated in repeating step (2) ~ (4) A Vmin
Throttle chink pressure when (6) confirming that the vibration damper controlled valve is driven valve for the first time p 1
According to vibration damper parameter in the step (4) and the needed adjustable damping hole area of design throttle slice thickness A Vh, confirm the throttle chink pressure when the vibration damper controlled valve is driven valve for the first time , wherein,
(7) confirm at controlled valve throttle valve plate Thickness Design speed point throttle chink pressure p fWith the piston hole flow Q h
According to vibration damper parameter, the needed adjustable damping hole area of design throttle slice thickness in the step (4) A VhAnd recovery stroke safety ratio η, confirm to do at the controlled valve block throttle chink of controlled valve throttle valve plate Thickness Design speed point pressure , and the piston hole flow does
Wherein, ;
(8) confirm the design thickness of controlled valve throttle valve plate
According to the normal open throttle hole area A 0, normal open orifice flow coefficient ε 0, the throttle chink pressure when the vibration damper controlled valve is driven valve for the first time p 1, at the controlled valve block throttle chink of controlled valve block Thickness Design speed point pressure p fWith the piston hole flow Q h, the valve block deformation coefficient G r , controlled valve block outer radius r BrAnd controlled valve port position radius r Kr, confirm the design thickness of controlled valve throttle valve plate
The advantage that the present invention has than existing technology:
Because the controlled valve of semi-active suspension controllable damper has adopted the parsing Optimization Design; So the design load of controlled valve parameter accurately and reliably; Avoid repetition test and modification; Thereby reduce the controllable damper design cost, shorten the controllable damper construction cycle, utilize this analytical optimization design method can satisfy the automotive semi-active suspension controllable damper fast and the requirement of precise design.
Description of drawings
Be described further below in conjunction with accompanying drawing in order to understand the present invention better.
Fig. 1 is controlled cylinder type hydraulic vibration damper controlled valve structure.
Fig. 2 is the controlled cylinder type hydraulic vibration damper of a semi-active suspension controlled valve method for optimally designing parameters flow chart.
Fig. 3 is the controllable damper speed characteristic curve.
Fig. 4 is the controllable damper indicator diagram.
Embodiment
Through an embodiment the present invention is done further explain below.
The sprung weight of certain automobile suspension system m 2=445kg; Unsprung weight m 1=38kg; Bearing spring rigidity K=29679N/m and tire stiffness K t=267112N/m; Vibration damper is installed lever ratio i=0.95; The vibration damper established angle θ=5 °; Annulus area between piston bore and the piston rod S r=3.02 * 10 -4m 2Cylinder bore D H=28mm; The piston gap length L H=9mm; The piston mean gap δ H=0.04mm; Eccentricity e=1.0; The fluid kinetic viscosity μ t=8.9 * 10 -3m 2Ps; Fluid density ρ=0.89 * 10 3Kg/m 3The piston hole number n h=4; The piston hole diameter d h=2mm; The piston hole equivalent length L He=5mm; The normal open throttle hole area A 0=0.2mm 2Normal open orifice flow coefficient ε 0=0.82; The adjustable damping orifice-metering coefficient ε v=0.82; Piston rod hole equivalent length L Ge=30mm; The piston rod bore dia d g=4mm; Restore stroke safety ratio η=1.39.
The controlled cylinder type hydraulic vibration damper of the semi-active suspension that the embodiment of the invention provided controlled valve Optimization Design, as shown in Figure 2, concrete steps are following:
(1) confirms the vehicle suspension system damping ratio
Sprung weight according to certain automobile suspension system m 2=445kg, unsprung weight m 1=38kg, bearing spring rigidity K=29679N/m and tire stiffness K t=267112N/m confirms suspension system travelling comfort optimum damping ratio =0.174, the Security optimum damping ratio =0.392, suspension system is optimized damping ratio ξ Op= ξ Oc+ 0.382 ( ξ Os- ξ Oc)=0.257, wherein, r k= K t/ K=9, r m= m 2/ m 1=11.8;
(2) order ξ= ξ Oc=0.174, what design vibration damper speed characteristics were restored stroke opens the valve damping constant
According to the suspension system sprung weight m 2=445kg, suspension rate K=29679N/m, vibration damper are installed lever ratio i=0.95, vibration damper established angle θ=5 °, what design vibration damper speed characteristics were restored stroke opens the valve damping constant =1359.5Ns/m;
(3) confirm the damping force of vibration damper when the golden section speed point
Open the valve damping constant according to what the vibration damper speed characteristics were restored stroke C k1 =1359.5Ns/m and golden section speed point V Gs=0.1854, confirm the damping force of vibration damper when the golden section speed point F Gs= C k1 V Gs=252.1N;
(4) confirm the design area in vibration damper adjustable damping hole
According to the annulus area between piston bore and the piston rod S r=3.02 * 10 -4m 2, cylinder bore D H=28mm, piston gap length L H=9mm, piston mean gap δ H=0.04mm, eccentricity e=1.0, fluid kinetic viscosity μ t=8.9 * 10 -3m 2Ps, piston hole number n h=4, piston hole diameter d h=2mm, piston hole equivalent length L He=5mm, normal open throttle hole area A 0=0.2mm 2, normal open orifice flow coefficient ε 0=0.82, adjustable damping orifice-metering coefficient ε v=0.82, piston rod hole equivalent length L Ge=30mm, piston rod bore dia d g=4mm reaches the damping force of vibration damper when the golden section speed point F Gs=252.1N confirms the design area in vibration damper adjustable damping hole A vFor
=1.0mm 2
Wherein, =1.224 * 10 -5, =7.101 * 10 -6, =1.655 * 10 16, =1.96 * 10 16
(5) order ξ= ξ Op, repeating step (2) ~ (4), the needed adjustable damping hole area of calculation Design throttle slice thickness A Vh=0.68mm 2Order ξ= ξ Os, adjustable damping Kongzui small size is calculated in repeating step (2) ~ (4) A Vmin=0.32mm 2
Throttle chink pressure when (6) confirming that the vibration damper controlled valve is driven valve for the first time p 1
According to vibration damper parameter in the step (4) and the needed adjustable damping hole area of design throttle slice thickness A v=0.68mm 2, confirm the throttle chink pressure when the vibration damper controlled valve is driven valve for the first time =1.98MPa, wherein,
=2.408×10 -5m -3/s;
(7) confirm at controlled valve throttle valve plate Thickness Design speed point valve block throttle chink pressure p fWith the piston hole flow Q h
According to vibration damper parameter, the needed adjustable damping hole area of design throttle slice thickness in the step (4) A Vh=0.68mm 2And recovery stroke safety ratio η=1.39, confirm at controlled valve throttle valve plate Thickness Design speed point throttle chink pressure =4.013MPa and piston hole flow
=1.0839 * 10 -4m 3/ s, wherein, =1222.56N;
(8) confirm the design thickness of controlled valve throttle valve plate
According to the normal open throttle hole area A 0=0.2mm 2, normal open orifice flow coefficient ε 0=0.82, valve block deformation coefficient G r =4.76 * 10 -22m 6/ N, controlled valve block outer radius r Br=8.5mm and controlled valve port position radius r Kr=8mm, fluid kinetic viscosity μ t=8.9 * 10 -3m 2Ps, fluid density ρ=0.89 * 10 3Kg/m 3, the throttle chink pressure when the vibration damper controlled valve is driven valve for the first time p 1=1.98MPa, at the controlled valve block throttle chink of controlled valve block Thickness Design speed point pressure p f=4.013MPa and piston hole flow Q h=1.0839 * 10 -4m 3/ s confirms the design thickness of controlled valve throttle valve plate
=0.3mm。
Utilize the comprehensive performance test bed controllable damper model machine of electro-hydraulic servo vibration damper to carry out characteristic test to design processing; Measured controllable damper speed characteristic curve and indicator diagram are respectively like Fig. 3 and shown in Figure 4; Two curves among the figure have satisfied automobile respectively and have taken best comfort and go maximum security; The controlled valve parameter designing value that the controlled cylinder type hydraulic vibration damper of this go-anywhere vehicle semi-active suspension is described is reliably, shows that controlled cylinder type hydraulic vibration damper controlled valve method for optimally designing parameters is correct.

Claims (4)

1. the controlled cylinder type hydraulic vibration damper of semi-active suspension controlled valve method for optimally designing parameters, its concrete steps are following:
(1) according to the sprung weight of vehicle suspension system m 2, unsprung weight m 1, bearing spring rigidity KAnd tire stiffness K t, confirm the optimization damping ratio of suspension system ξ Op= ξ Oc+ 0.382 ( ξ Os- ξ Oc), wherein, , , ,
(2) according to the suspension system sprung weight m 2, suspension rate K, vibration damper installs lever ratio i, the vibration damper established angle θ, what design vibration damper speed characteristics were restored stroke opens the valve damping constant , wherein, ξ= ξ Oc
(3) open the valve damping constant according to what the vibration damper speed characteristics were restored stroke C k1 And golden section speed point V Gs=0.618 C k1 , confirm the damping force of vibration damper when the golden section speed point F Gs= C k1 V Gs
(4) according to the annulus area between piston bore and the piston rod S r, cylinder bore D H, the piston gap length L H, the piston mean gap δ H, eccentricity e, fluid density ρ,The fluid kinetic viscosity μ t, the piston hole number n h, the piston hole diameter d h, the piston hole equivalent length L He, the normal open throttle hole area A 0, normal open orifice flow coefficient ε 0, the adjustable damping orifice-metering coefficient ε v, piston rod hole equivalent length L Ge, the piston rod bore dia d gReach the damping force of vibration damper when the golden section speed point F Gs, confirm the design area in vibration damper adjustable damping hole A vFor
; Wherein
(5) order ξ= ξ Op, repeating step (2) ~ (4), the area in needed adjustable damping hole when calculating the throttle slice thickness design A Vh
(6) order ξ= ξ Os, the minimum area in adjustable damping hole is calculated in repeating step (2) ~ (4) A Vmin
(7) according to the needed adjustable damping hole area of design throttle slice thickness that obtains in vibration damper parameter in the step (4) and the step (5) A v, confirm the throttle chink pressure when the vibration damper controlled valve is driven valve for the first time , wherein,
(8) according to vibration damper parameter, the needed adjustable damping hole area of design throttle slice thickness in the step (4) A vAnd recovery stroke safety ratio η, confirm at controlled valve throttle valve plate Thickness Design speed point valve block throttle chink pressure With the piston hole flow
; Wherein, ;
(9) according to the normal open throttle hole area A 0, normal open orifice flow coefficient ε 0, the throttle chink pressure when the vibration damper controlled valve is driven valve for the first time p 1, at controlled valve throttle valve plate Thickness Design speed point valve block throttle chink pressure p fWith the piston hole flow Q h, the valve block deformation coefficient G r , controlled valve block outer radius r BrAnd controlled valve port position radius r Kr, confirm the design thickness of controlled valve throttle valve plate
2. according to the step (1) in the said method of claim 1, it is characterized in that: according to the sprung weight of vehicle suspension system m 2, unsprung weight m 1, bearing spring rigidity KAnd tire stiffness K t, confirm the optimization damping ratio of suspension system ξ Op= ξ Oc+ 0.382 ( ξ Os- ξ Oc), wherein, ξ OsBe the safest damping ratio of suspension system, ξ OcBe suspension system the most comfortable damping ratio.
3. according to the step (2) in the said method of claim 1 ~ step (4), it is characterized in that: when damping ratio is got respectively ξ Oc, ξ OpWith ξ OsThe time, can obtain the design area in controllable damper adjustable damping hole respectively A v, throttle slice thickness needed adjustable damping of when design hole area A VhMinimum area with the adjustable damping hole A Vmin
4. according to the step (9) in the said method of claim 1, it is characterized in that: according to the normal open throttle hole area A 0, normal open orifice flow coefficient ε 0, the throttle chink pressure when the vibration damper controlled valve is driven valve for the first time p 1, at controlled valve throttle valve plate Thickness Design speed point valve block throttle chink pressure p fWith the piston hole flow Q h, the valve block deformation coefficient G r , controlled valve block outer radius r BrAnd controlled valve port position radius r Kr, confirm the design thickness of controlled valve throttle valve plate h
CN201210357768.5A 2012-07-18 2012-09-25 Optimal design method for parameter of controllable cylinder type hydraulic buffer of semi-active suspension CN102840265B (en)

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CN103133589A (en) * 2013-03-08 2013-06-05 山东理工大学 Method for designing maximum limiting interval of rebound valve of hydraulic vibration absorber
CN103133588A (en) * 2013-03-08 2013-06-05 山东理工大学 Method for calculating local pressure loss and piston hole equivalent length of hydraulic vibration absorber
CN103148147A (en) * 2013-03-08 2013-06-12 山东理工大学 Design method for rebound valve plate thickness of hydraulic oscillating damper
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CN103148149A (en) * 2013-03-15 2013-06-12 山东理工大学 Design method for thickness of limiting clearance gasket of automobile damper compression valve
CN104832489A (en) * 2015-03-27 2015-08-12 上海理工大学 Method for manufacturing oil cylinder of movable arm of excavator
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CN105946491A (en) * 2016-06-21 2016-09-21 上汽通用汽车有限公司 Vehicle suspension parameter determining method
US9662954B2 (en) 2012-11-07 2017-05-30 Polaris Industries Inc. Vehicle having suspension with continuous damping control
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US10406884B2 (en) 2017-06-09 2019-09-10 Polaris Industries Inc. Adjustable vehicle suspension system
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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9662954B2 (en) 2012-11-07 2017-05-30 Polaris Industries Inc. Vehicle having suspension with continuous damping control
US9205717B2 (en) 2012-11-07 2015-12-08 Polaris Industries Inc. Vehicle having suspension with continuous damping control
US10005335B2 (en) 2012-11-07 2018-06-26 Polaris Industries Inc. Vehicle having suspension with continuous damping control
CN103115104A (en) * 2013-03-08 2013-05-22 山东理工大学 Design method for maximum allowable thickness of absorber recovery sandwich plate valve sheet
CN103133589A (en) * 2013-03-08 2013-06-05 山东理工大学 Method for designing maximum limiting interval of rebound valve of hydraulic vibration absorber
CN103115105B (en) * 2013-03-08 2014-09-03 山东理工大学 Splitting design method for absorber recovery sandwich plate valve sheet
CN103115105A (en) * 2013-03-08 2013-05-22 山东理工大学 Splitting design method for absorber recovery sandwich plate valve sheet
CN103133588A (en) * 2013-03-08 2013-06-05 山东理工大学 Method for calculating local pressure loss and piston hole equivalent length of hydraulic vibration absorber
CN103148147A (en) * 2013-03-08 2013-06-12 山东理工大学 Design method for rebound valve plate thickness of hydraulic oscillating damper
CN103148154A (en) * 2013-03-15 2013-06-12 山东理工大学 Design method for annular superposed valve plate of automobile damper compression valve
CN103148149A (en) * 2013-03-15 2013-06-12 山东理工大学 Design method for thickness of limiting clearance gasket of automobile damper compression valve
CN104832489A (en) * 2015-03-27 2015-08-12 上海理工大学 Method for manufacturing oil cylinder of movable arm of excavator
US10124709B2 (en) 2015-05-15 2018-11-13 Polaris Industries Inc. Utility vehicle
CN105946491B (en) * 2016-06-21 2018-05-18 上汽通用汽车有限公司 A kind of definite method of vehicle suspension parameters
CN105946491A (en) * 2016-06-21 2016-09-21 上汽通用汽车有限公司 Vehicle suspension parameter determining method
US10406884B2 (en) 2017-06-09 2019-09-10 Polaris Industries Inc. Adjustable vehicle suspension system
US10946736B2 (en) 2018-06-05 2021-03-16 Polaris Industries Inc. All-terrain vehicle

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