CN103244600B - Design method of turn number of electromagnetic coil of automotive magneto-rheological semi-active suspension - Google Patents
Design method of turn number of electromagnetic coil of automotive magneto-rheological semi-active suspension Download PDFInfo
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- CN103244600B CN103244600B CN201310212217.4A CN201310212217A CN103244600B CN 103244600 B CN103244600 B CN 103244600B CN 201310212217 A CN201310212217 A CN 201310212217A CN 103244600 B CN103244600 B CN 103244600B
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Abstract
The invention relates to a design method of the turn number of an electromagnetic coil of an automotive magneto-rheological semi-active suspension, and belongs to the technical field of dampers. The design method is characterized by comprising the steps that optimal suspension damping ratios based on comfortability and safety are determined respectively according to single-wheel 1/4 automobile parameters; the required maximum Coulomb damping force of a semi-active suspension magneto-rheological damper under a condition of the maximum speed is determined according to a suspension lever ratio and a mounting angle of the magneto-rheological damper; and an optimal design is conducted on the turn number N of the electromagnetic coil of the automotive magneto-rheological semi-active suspension according to relations among the Coulomb damping force, a structure parameter and a magneto-rheological liquid characteristic parameter of the damper, and the maximum control current Imax. A reliable design value of the turn number N of the electromagnetic coil can be obtained with the adoption of the design method of the turn number of the electromagnetic coil; a design level, the design level, the quality and the performances of a magneto-rheological semi-active suspension system are raised and improved; a design requirement of ensuring the traveling smoothness of an automobile under the condition of the maximum control current is met; and the design and testing expenses can be lowered.
Description
Technical field
The present invention relates to magneto-rheological semiactive suspension system, particularly the design method of the Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn.
Background technique
Magneto-rheological vibration damper can be realized the control to damping force by controlling the size of electric current, it has the features such as fast response time, low in energy consumption, regulation range is large, and operating conditions is relatively simple, become a focus of Present Domestic, outer Vehicle Semi-active Suspension research field.The electromagnetic coil number of turn
nand electric current
isize determining the damping characteristic of magneto-rheological vibration damper and the damping of semi-active suspension system coupling, vehicle running smoothness is had to material impact.Although lot of domestic and international vehicle suspension researcher had once carried out large quantity research to Automobile Magnetorheological Semi-active Suspension, but owing to being subject to the restriction of semi-active suspension system optimum damping ratio, fail to provide the design method of reliable Automobile Magnetorheological Semi-active Suspension electromagnetic coil always, according to consulted reference materials known, home and abroad is to Automobile Magnetorheological Semi-active Suspension systematic research at present, mostly concentrate on the research of control strategy and controlling method, and for the electromagnetic coil number of turn
n, be mostly but the method by repetition test, finally determine the electromagnetic coil number of turn
nparameter designing value.Along with the fast development of automotive industry and improving constantly of Vehicle Speed, magneto-rheological semiactive suspension system is had higher requirement, therefore, must set up a kind of accurate, reliable Automobile Magnetorheological Semi-active Suspension electromagnetic coil
ndesign method, reduce design and testing expenses, improve designing quality, level and the performance of magneto-rheological semiactive suspension system, improve the run smoothness of vehicle.
Summary of the invention
For the defect existing in above-mentioned prior art, technical problem to be solved by this invention is to provide a kind of design method of the reliable Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn.
In order to solve the problems of the technologies described above, the design method of the Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn provided by the present invention, its technological scheme implementation step is as follows:
(1) determine the semi-active suspension optimum damping ratio based on travelling comfort
:
According to the suspension sprung weight of single-wheel 1/4 vehicle
m 2, unsprung weight
m 1and mass ratio
r m=
m 2 / m 1, and suspension rate
k 2, tire stiffness
k tand ratio of rigidity
r k=
k t / k 2, determine the semi-active suspension optimum damping ratio based on travelling comfort
, that is:
；
(2) determine the semi-active suspension optimum damping ratio based on Security
:
According to the suspension sprung weight of single-wheel 1/4 vehicle
m 2, unsprung weight
m 1and mass ratio
r m=
m 2 / m 1, and suspension rate
k 2, tire stiffness
k tand ratio of rigidity
r k=
k t / k 2, determine the semi-active suspension optimum damping ratio based on Security
, that is:
；
(3) determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
:
According to the suspension sprung weight of single-wheel 1/4 vehicle
m 2, suspension rate
k 2, suspension lever ratio
i, vibration damper setting angle
θ, vibration damper top speed
v max, in step (1)
and in step (2)
, determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
, that is:
；
(4) the automobile magnetic current semi-active suspension electromagnetic coil number of turn
noptimal design:
According to the diameter of magneto-rheological vibration damper piston bore
d h, the annular space between piston and cylinder barrel
h, piston length
l, diameter of piston rod
d g, the shear stress coefficient of magnetic rheological liquid
and magnetic intensity index
, electromagnetic coil maximum controlling current
i max, and in step (3)
f imax, the number of turn to Automobile Magnetorheological Semi-active Suspension electromagnetic coil
nbe optimized design, that is:
。
The present invention has advantages of than prior art:
Although lot of domestic and international vehicle suspension researcher had once carried out large quantity research to Automobile Magnetorheological Semi-active Suspension, but owing to being subject to the restriction of semi-active suspension system optimum damping ratio, fail to provide the design method of reliable Automobile Magnetorheological Semi-active Suspension electromagnetic coil always, according to consulted reference materials known, home and abroad is to Automobile Magnetorheological Semi-active Suspension systematic research at present, mostly concentrate on the research of control strategy and controlling method, and for the electromagnetic coil number of turn
nbe mostly the method by repetition test, finally determine the electromagnetic coil number of turn
nparameter designing value.Therefore, the current design method of magneto-rheological semiactive suspension electromagnetic coil, is difficult to meet the proposed designing requirement that improves constantly of the fast development of automotive industry and Vehicle Speed.The design method of this Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn, first according to the sprung weight of vehicle suspension, unsprung weight, suspension rate and tire stiffness, determines respectively the automotive semi-active suspension optimum damping ratio based on travelling comfort
with the semi-active suspension optimum damping ratio based on Security
; Then, vehicle suspension lever ratio
i, vibration damper setting angle
θ, vibration damper top speed
v max, the optimum damping ratio based on travelling comfort
and the optimum damping ratio based on Security
, determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
; Subsequently, according to the needed maximum Coulomb damping power of magneto-rheological vibration damper
f imax
with structural parameter, magnetic rheological liquid special parameter, electromagnetic coil maximum controlling current
i maxbetween relation, to the Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn
nbe optimized design.Utilize the design method of this Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn, can design and obtain the reliable electromagnetic coil number of turn
ndesign load, in maximum controlling current situation, guarantee vehicle running smoothness and security requirement, meanwhile, can also reduce design and the testing expenses of Vehicle Semi-active Suspension System, improve design level, the quality and performance of Automobile Magnetorheological Semi-active Suspension system.
In order to understand better the present invention, below in conjunction with accompanying drawing, be further described.
Fig. 1 is the structure principle chart of automotive semi-active suspension magneto-rheological vibration damper;
Fig. 2 is the design flow diagram of the Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn;
Fig. 3 is embodiment one automotive semi-active suspension magneto-rheological vibration damper damping characteristic simulation curve;
Fig. 4 is embodiment two automotive semi-active suspension magneto-rheological vibration damper damping characteristic simulation curve;
Fig. 5 is embodiment three automotive semi-active suspension magneto-rheological vibration damper damping characteristic simulation curve;
Fig. 6 is embodiment four automotive semi-active suspension magneto-rheological vibration damper damping characteristic simulation curve.
Specific embodiments
Below by embodiment, the present invention is described in further detail.
Embodiment one: the structural principle of certain automotive semi-active suspension magneto-rheological vibration damper, as shown in Figure 1, and damper piston cylinder barrel 1, piston 2, electromagnetic coil 3, piston rod 4, wherein, electromagnetic coil 3 is embedded in the middle part of piston, its number of turn
nbe semi-active suspension magneto-rheological vibration damper key design parameter.The sprung weight of this automobile single-wheel suspension
m 2=300kg, suspension rate
k 2=13057N/m, unsprung weight
m 1=40kg, tire stiffness
k t=192000N/m; The internal diameter of the piston bore of magneto-rheological vibration damper is
d h=28mm, diameter of piston rod
d g=18mm, the annular space between piston and inner cylinder tube
h=0.9mm, piston length
l=40mm; Suspension lever ratio
i=0.9, vibration damper setting angle
=10 °, vibration damper top speed
v max=1.0m/s; Electromagnetic coil maximum controlling current
i max=2.0A, the initial viscosity of magnetic rheological liquid is 0.8Pa.s, shear stress coefficient
=0.0015, magnetic intensity index
=1.6.To this auto magnetorheological vibration damper electromagnetic coil number of turn
nbe optimized design.
The design method of the Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn that example of the present invention provides, its electromagnetic coil number of turn
ndesign flow diagram as shown in Figure 2, concrete steps are as follows:
(1) determine the semi-active suspension optimum damping ratio based on travelling comfort
:
According to the suspension sprung weight of this automobile single-wheel 1/4 vehicle
m 2=300kg, unsprung weight
m 1=40kg and mass ratio
r m=
m 2 / m 1=7.5, and suspension rate
k 2=13057N/m, tire stiffness
k t=192000N/m and ratio of rigidity
r k=
k t / k 2=14.7, determine the semi-active suspension optimum damping ratio based on travelling comfort
, that is:
＝0.1388；
(2) determine the semi-active suspension optimum damping ratio based on Security
:
According to the sprung weight of single-wheel 1/4 vehicle
m 2=300kg, unsprung weight
m 1=40kg and mass ratio
r m=
m 2 / m 1=7.5, and suspension rate
k 2=13057N/m, tire stiffness
k t=192000N/m and ratio of rigidity
r k=
k t / k 2=14.7, determine the semi-active suspension optimum damping ratio based on Security
, that is:
＝0.5848；
(3) determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
:
According to the sprung weight of single-wheel 1/4 vehicle
m 2=300kg, suspension rate
k 2=13057N/m, suspension lever ratio
i=0.9, vibration damper setting angle
θ=10 °, vibration damper top speed
v max=1.0m/s, in step (1)
=0.1388 and step (2) in
=0.5848, determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
, that is:
＝2247.5N；
(4) the automobile magnetic current semi-active suspension electromagnetic coil number of turn
noptimal design:
According to the diameter of magneto-rheological vibration damper piston bore
d h=28mm, the annular space between piston and cylinder barrel
h=0.9mm, piston length
l=40mm, diameter of piston rod
d g=18mm, shear stress coefficient
=0.0015, the magnetic intensity index of shear stress
=1.6, electromagnetic coil maximum controlling current
i max=2.0A, and in step (3)
f imax=2247.5N, the number of turn to this Automobile Magnetorheological Semi-active Suspension electromagnetic coil
nbe optimized design, that is:
=100.69 circles;
Right
ncarry out rounding, optimal design value that can this Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn is
n=101 circles.
According to the initial viscosity of designed electromagnetic coil number of turn N=101 circle, maximum controlling current, damper structure parameter, magnetic rheological liquid special parameter and magnetic rheological liquid, be 0.8Pa.s, utilize damping characteristic simulated program, the damping characteristic curve of resulting this automotive semi-active suspension magneto-rheological vibration damper of emulation, as shown in Figure 3, wherein, maximum total damping power
f max=2759.9N, maximum Coulomb damping power
f imax
=2258.6N, the damping ratio of Vehicle Semi-active Suspension System
=0.5477, desired with design
=0.5848 matches.The design method that shows this Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn is correct, reliable.
Embodiment two: the sprung weight of certain automobile single-wheel suspension
m 2=350kg, suspension rate
k 2=16719N/m, unsprung weight
m 1=40kg, tire stiffness
k t=192000N/m; Suspension lever ratio
i=0.9 and vibration damper setting angle
=10 °, the piston bore internal diameter of magneto-rheological vibration damper, diameter of piston rod, piston length are identical with embodiment's one, and piston bore internal diameter is
d h=28mm, diameter of piston rod
d g=18mm, piston length
l=40mm; Annular space between piston and cylinder barrel
h=0.8mm; Vibration damper top speed
v max=1.0m/s; The initial viscosity of magnetic rheological liquid is 0.8Pa.s, shear stress coefficient
=0.0015, magnetic intensity index
=1.6; Electromagnetic coil maximum controlling current
i max=2.0A.To this automotive semi-active suspension magneto-rheological vibration damper electromagnetic coil number of turn
nbe optimized design.
Adopt embodiment one design procedure, to this automotive semi-active suspension magneto-rheological vibration damper electromagnetic coil number of turn
ndesign, that is:
(1) determine the semi-active suspension optimum damping ratio based on travelling comfort
:
According to the suspension sprung weight of this automobile single-wheel 1/4 vehicle
m 2=350kg, unsprung weight
m 1=40kg and mass ratio
r m=
m 2 / m 1=8.75, and suspension rate
k 2=16719N/m, tire stiffness
k t=192000N/m and ratio of rigidity
r k=
k t / k 2=11.48, determine the semi-active suspension optimum damping ratio based on travelling comfort
, that is:
＝0.1557；
(2) determine the semi-active suspension optimum damping ratio based on Security
:
According to the sprung weight of single-wheel 1/4 vehicle
m 2=350kg, unsprung weight
m 1=40kg and mass ratio
r m=
m 2 / m 1=8.75, and suspension rate
k 2=16719N/m, tire stiffness
k t=192000N/m and ratio of rigidity
r k=
k t / k 2=14.48, determine the semi-active suspension optimum damping ratio based on Security
, that is:
＝0.4871；
(3) determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
:
According to the sprung weight of single-wheel 1/4 vehicle
m 2=350kg, suspension rate
k 2=16719N/m, suspension lever ratio
i=0.9, vibration damper setting angle
θ=10 °, vibration damper top speed
v max=1.0m/s, in step (1)
=0.1557 and step (2) in
=0.4871, determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
, that is:
＝2040.5N；
(4) the automobile magnetic current semi-active suspension electromagnetic coil number of turn
noptimal design:
According to the diameter of magneto-rheological vibration damper piston bore
d h=28mm, the annular space between piston and cylinder barrel
h=0.8mm, piston length
l=40mm, diameter of piston rod
d g=18mm, the shear stress coefficient of magnetic rheological liquid
=0.0015, magnetic intensity index
=1.6, electromagnetic coil maximum controlling current
i max=2.0A, and in step (3)
f imax=2040.5N, the number of turn to this Automobile Magnetorheological Semi-active Suspension electromagnetic coil
nbe optimized design, that is:
=76.889 circles;
Right
ncarry out rounding, optimal design value that can this Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn is
n=77 circles.
According to the designed electromagnetic coil number of turn
nthe initial viscosity of=77 circles, maximum controlling current, damper structure parameter, magnetic rheological liquid special parameter and magnetic rheological liquid is 0.8Pa.s, utilize damping characteristic simulated program, the damping characteristic curve of resulting this automotive semi-active suspension magneto-rheological vibration damper of emulation, as shown in Figure 4, wherein, maximum total damping power
f max=2798.3N, maximum Coulomb damping power
f imax
=2045.2N, the damping ratio of Vehicle Semi-active Suspension System
=0.4544, desired with design
=0.4871 matches.
Embodiment three: the sprung weight of certain automobile single-wheel suspension
m 2=400kg, suspension rate
k 2=20884N/m, unsprung weight
m 1=40kg, tire stiffness
k t=192000N/m; Suspension lever ratio
i=0.9 and vibration damper setting angle
=10 °, the piston bore internal diameter of magneto-rheological vibration damper is
d h=28mm, diameter of piston rod
d g=20mm, piston length
l=40mm; Annular space between piston and cylinder barrel
h=0.7mm; Vibration damper top speed
v max=1.0m/s; The initial viscosity of magnetic rheological liquid is 0.8Pa.s, shear stress coefficient
=0.0015, magnetic intensity index
=1.6; Electromagnetic coil maximum controlling current
i max=2.0A.To this automotive semi-active suspension magneto-rheological vibration damper electromagnetic coil number of turn
nbe optimized design.
Adopt embodiment one design procedure, to this automotive semi-active suspension magneto-rheological vibration damper electromagnetic coil number of turn
ndesign, that is:
(1) determine the semi-active suspension optimum damping ratio based on travelling comfort
:
According to the suspension sprung weight of this automobile single-wheel 1/4 vehicle
m 2=400kg, unsprung weight
m 1=40kg and mass ratio
r m=
m 2 / m 1=10, and suspension rate
k 2=20884N/m, tire stiffness
k t=192000N/m and ratio of rigidity
r k=
k t / k 2=9.1936, determine the semi-active suspension optimum damping ratio based on travelling comfort
, that is:
＝0.173；
(2) determine the semi-active suspension optimum damping ratio based on Security
:
According to the sprung weight of single-wheel 1/4 vehicle
m 2=400kg, unsprung weight
m 1=40kg and mass ratio
r m=
m 2 / m 1=10, and suspension rate
k 2=20884N/m, tire stiffness
k t=192000N/m and ratio of rigidity
r k=
k t / k 2=9.1936, determine the semi-active suspension optimum damping ratio based on Security
, that is:
＝0.4176；
(3) determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
:
According to the sprung weight of single-wheel 1/4 vehicle
m 2=400kg, suspension rate
k 2=20884N/m, suspension lever ratio
i=0.9, vibration damper setting angle
θ=10 °, vibration damper top speed
v max=1.0m/s, in step (1)
=0.173 and step (2) in
=0.41761, determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
, that is:
＝1800.4N；
(4) the automobile magnetic current semi-active suspension electromagnetic coil number of turn
noptimal design:
According to the diameter of magneto-rheological vibration damper piston bore
d h=28mm, the annular space between piston and cylinder barrel
h=0.7mm, piston length
l=40mm, diameter of piston rod
d g=20mm, the shear stress coefficient of magnetic rheological liquid
=0.0015, the magnetic intensity index of shear stress
=1.6, electromagnetic coil maximum controlling current
i max=2.0A, and in step (3)
f imax=1800.4N, the number of turn to this Automobile Magnetorheological Semi-active Suspension electromagnetic coil
nbe optimized design, that is:
=64.563 circles;
Right
ncarry out rounding, optimal design value that can this Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn is
n=65 circles.
According to the designed electromagnetic coil number of turn
nthe initial viscosity of=65 circles, maximum controlling current, damper structure parameter, magnetic rheological liquid special parameter and magnetic rheological liquid is 0.8Pa.s, utilize damping characteristic simulated program, the damping characteristic curve of resulting this automotive semi-active suspension magneto-rheological vibration damper of emulation, as shown in Figure 5, wherein, maximum total damping power
f max=2581.6N, maximum Coulomb damping power
f imax
=1819.9N, the damping ratio of Vehicle Semi-active Suspension System
=0.3508, desired with design
=0.4176 matches.
Embodiment four: certain automobile single-wheel suspension parameter is identical with embodiment three, i.e. sprung weight
m 2=400kg, suspension rate
k 2=20884N/m, unsprung weight
m 1=40kg, tire stiffness
k t=192000N/m; Suspension lever ratio
i=0.95 and vibration damper setting angle
=8 °, the piston bore internal diameter of magneto-rheological vibration damper is
d h=28mm, diameter of piston rod
d g=18mm, piston length
l=40mm; Annular space between piston and cylinder barrel
h=0.7mm; Vibration damper top speed
v max=1.0m/s; The shear stress coefficient of magnetic rheological liquid
=0.002, magnetic intensity index
=1.5; Electromagnetic coil maximum controlling current
i max=2.0A.To this automotive semi-active suspension magneto-rheological vibration damper electromagnetic coil number of turn
nbe optimized design.
Adopt embodiment one design procedure, to this automotive semi-active suspension magneto-rheological vibration damper electromagnetic coil number of turn
ndesign, that is:
(1) determine the semi-active suspension optimum damping ratio based on travelling comfort
:
Because the single-wheel suspension parameter of this automobile is identical with embodiment three, therefore, the desired semi-active suspension optimum damping ratio based on travelling comfort
also identical with embodiment three, that is:
＝0.1730；
(2) determine the semi-active suspension optimum damping ratio based on Security
:
Because the single-wheel suspension parameter of this automobile is identical with embodiment three, therefore, the desired semi-active suspension optimum damping ratio based on Security
also identical with embodiment three, that is:
＝0.4176；
(3) determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
:
According to the sprung weight of single-wheel 1/4 vehicle
m 2=400kg, suspension rate
k 2=20884N/m, suspension lever ratio
i=0.95, vibration damper setting angle
θ=8 °, vibration damper top speed
v max=1.0m/s, in step (1)
=0.1730 and step (2) in
=0.4176, determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
f imax
, that is:
＝1598.1N；
(4) the automobile magnetic current semi-active suspension electromagnetic coil number of turn
noptimal design:
According to the diameter of magneto-rheological vibration damper piston bore
d h=28mm, the annular space between piston and cylinder barrel
h=0.7mm, piston length
l=40mm, diameter of piston rod
d g=18mm, the shear stress coefficient of magnetic rheological liquid
=0.002, the magnetic intensity index of shear stress
=1.5, electromagnetic coil maximum controlling current
i max=2.0A, and in step (3)
f imax=1598.1N, the number of turn to this Automobile Magnetorheological Semi-active Suspension electromagnetic coil
nbe optimized design, that is:
=86.9 circles;
Right
ncarry out rounding, optimal design value that can this Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn is
n=87 circles.
According to the designed electromagnetic coil number of turn
nthe initial viscosity of=87 circles, maximum controlling current, damper structure parameter, magnetic rheological liquid special parameter and magnetic rheological liquid is 0.8Pa.s, shear stress coefficient
=0.002, magnetic intensity index
=1.5; Utilize damping characteristic simulated program, the damping characteristic curve of resulting this automotive semi-active suspension magneto-rheological vibration damper of emulation, as shown in Figure 6, and wherein, maximum total damping power
f max=2784.6N, maximum Coulomb damping power
f imax
=1600N, the damping ratio of Vehicle Semi-active Suspension System
=0.4263, respectively with the desired maximum Coulomb damping power of design
f imax
=1598.1N and suspension damping ratio
=0.4176 matches.The design method that shows this Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn is correct, reliable.
Claims (1)
1. the design method of the Automobile Magnetorheological Semi-active Suspension electromagnetic coil number of turn, its specific design step is as follows:
(1) determine the semi-active suspension optimum damping ratio ξ based on travelling comfort
c:
According to the suspension sprung weight m of single-wheel 1/4 vehicle
2, unsprung weight m
1and mass ratio r
m=m
2/ m
1, and suspension rate k
2, tire stiffness k
tand ratio of rigidity r
k=k
t/ k
2, determine the semi-active suspension optimum damping ratio ξ based on travelling comfort
c, that is:
(2) determine the semi-active suspension optimum damping ratio ξ based on Security
s:
According to the suspension sprung weight m of single-wheel 1/4 vehicle
2, unsprung weight m
1and mass ratio r
m=m
2/ m
1, and suspension rate k
2, tire stiffness k
twith ratio of rigidity r
k=k
t/ k
2, determine the semi-active suspension optimum damping ratio ξ based on Security
s, that is:
(3) determine the needed maximum Coulomb damping power F of semi-active suspension magneto-rheological vibration damper
imax:
According to the suspension sprung weight m of single-wheel 1/4 vehicle
2, suspension rate k
2, suspension lever ratio i, vibration damper setting angle θ, vibration damper top speed V
max, the ξ in step (1)
cand the ξ in step (2)
s, determine the needed maximum Coulomb damping power F of semi-active suspension magneto-rheological vibration damper
imax, that is:
(4) optimal design of automobile magnetic current semi-active suspension electromagnetic coil number of turn N:
According to the diameter D of magneto-rheological vibration damper piston bore
h, the annular space h between piston and cylinder barrel, piston length L, diameter of piston rod d
g, the shear stress COEFFICIENT K of magnetic rheological liquid
τand magnetic intensity index α, electromagnetic coil maximum controlling current I
max, and the F in step (3)
imax, the number of turn N of Automobile Magnetorheological Semi-active Suspension electromagnetic coil is optimized to design, that is:
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| CN101622548A (en) * | 2007-03-02 | 2010-01-06 | Qed国际科技公司 | Be used to measure the method and apparatus of the magnetic permeability of material |
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