CN103244600A - 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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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 the magneto-rheological semiactive suspension system, particularly the design method of the auto magnetorheological semi-active suspension electromagnetic coil number of turn.
Background technique
Magneto-rheological vibration damper can be realized the control to damping force by the size of control electric current, it has characteristics such as speed of response is fast, low in energy consumption, regulation range is big, and operating conditions is simple relatively, has become a focus of current home and abroad vehicle semi-active suspension research field.The electromagnetic coil number of turn
NAnd electric current
ISize determining the damping coupling of the damping characteristic of magneto-rheological vibration damper and semi-active suspension system vehicle running smoothness to be had material impact.Although lot of domestic and international vehicle suspension researcher had once carried out big quantity research to the auto magnetorheological semi-active suspension, but owing to be subjected to the restriction of semi-active suspension system optimum damping ratio, fail to provide the design method of reliable auto magnetorheological semi-active suspension electromagnetic coil always, according to consult reference materials as can be known, the home and abroad is to the research of auto magnetorheological semi-active suspension system at present, mostly concentrate on the research of control strategy and controlling method, and for the electromagnetic coil number of turn
N, but mostly be the method by repetition test, finally determine the electromagnetic coil number of turn
NThe parameter designing value.Along with improving constantly of rapid development of automobile industry and Vehicle Speed, system has higher requirement to magneto-rheological semiactive suspension, therefore, must set up a kind of accurate, reliable auto 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
At the defective that exists in the above-mentioned prior art, technical problem to be solved by this invention provides a kind of design method of the reliable auto 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 auto magnetorheological semi-active suspension electromagnetic coil number of turn provided by the present invention, its technological scheme implementation step is as follows:
(1) definite semi-active suspension optimum damping ratio based on travelling comfort
:
Suspension sprung weight according to 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) definite semi-active suspension optimum damping ratio based on Security
:
Suspension sprung weight according to 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
:
Suspension sprung weight according to single-wheel 1/4 vehicle
m 2, suspension rate
k 2, the suspension lever ratio
i, the vibration damper setting angle
θ, the vibration damper top speed
V Max, in the step (1)
And in the 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:
Diameter according to the magneto-rheological vibration damper piston bore
D H, the annular space between piston and the cylinder barrel
h, piston length
L, diameter of piston rod
d g, the mangneto shearing stress coefficient of magnetic rheological liquid
And magnetic intensity index
, the electromagnetic coil maximum controlling current
I Max, and in the step (3)
F Imax, to the number of turn of auto magnetorheological semi-active suspension electromagnetic coil
NBe optimized design, that is:
The advantage that the present invention has than prior art:
Although lot of domestic and international vehicle suspension researcher had once carried out big quantity research to the auto magnetorheological semi-active suspension, but owing to be subjected to the restriction of semi-active suspension system optimum damping ratio, fail to provide the design method of reliable auto magnetorheological semi-active suspension electromagnetic coil always, according to consult reference materials as can be known, the home and abroad is to the research of auto magnetorheological semi-active suspension system at present, mostly concentrate on the research of control strategy and controlling method, and for the electromagnetic coil number of turn
NMostly be the method by repetition test, finally determine the electromagnetic coil number of turn
NThe parameter designing value.Therefore, the design method of magneto-rheological semiactive suspension electromagnetic coil is difficult to satisfy the designing requirement that improving constantly of rapid development of automobile industry and Vehicle Speed proposes at present.The design method of this auto magnetorheological semi-active suspension electromagnetic coil number of turn at first according to sprung weight, unsprung weight, suspension rate and the tire stiffness of vehicle suspension, is determined the automotive semi-active suspension optimum damping ratio based on travelling comfort respectively
With the semi-active suspension optimum damping ratio based on Security
Then, vehicle suspension lever ratio
i, the vibration damper setting angle
θ, the vibration damper top speed
V Max, based on the optimum damping ratio of travelling comfort
Reach 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 the relation, to the auto magnetorheological semi-active suspension electromagnetic coil number of turn
NBe optimized design.Utilize the design method of this auto magnetorheological semi-active suspension electromagnetic coil number of turn, can design and obtain the reliable electromagnetic coil number of turn
NDesign load, under the maximum controlling current situation, guarantee vehicle running smoothness and security requirement, simultaneously, can also reduce design and the testing expenses of Vehicle Semi-active Suspension System, improve design level, quality and the performance of auto magnetorheological semi-active suspension system.
Be further described below in conjunction with accompanying drawing in order to understand the present invention better.
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 auto 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 middle 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 the inner cylinder tube
h=0.9mm, piston length
L=40mm; The suspension lever ratio
I=0.9, the vibration damper setting angle
=10 °, vibration damper top speed
V Max=1.0m/s; The electromagnetic coil maximum controlling current
I Max=2.0A, the initial viscosity of magnetic rheological liquid are 0.8Pa.s, mangneto shearing stress coefficient
=0.0015, the magnetic intensity index
=1.6.To this auto magnetorheological vibration damper electromagnetic coil number of turn
NBe optimized design.
The design method of the auto 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) definite semi-active suspension optimum damping ratio based on travelling comfort
:
Suspension sprung weight according to 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:
(2) definite semi-active suspension optimum damping ratio based on Security
:
Sprung weight according to 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:
(3) determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
F IMax
:
Sprung weight according to single-wheel 1/4 vehicle
m 2=300kg, suspension rate
k 2=13057N/m, the suspension lever ratio
I=0.9, the vibration damper setting angle
θ=10 °, the vibration damper top speed
V Max=1.0m/s, in the 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:
(4) the automobile magnetic current semi-active suspension electromagnetic coil number of turn
NOptimal design:
Diameter according to the magneto-rheological vibration damper piston bore
D H=28mm, the annular space between piston and the cylinder barrel
h=0.9mm, piston length
L=40mm, diameter of piston rod
d g=18mm, mangneto shearing stress coefficient
=0.0015, the magnetic intensity index of mangneto shearing stress
=1.6, the electromagnetic coil maximum controlling current
I Max=2.0A, and in the step (3)
F Imax=2247.5N is to the number of turn of this auto magnetorheological semi-active suspension electromagnetic coil
NBe optimized design, that is:
Right
NCarry out rounding, optimal design value that can this auto magnetorheological semi-active suspension electromagnetic coil number of turn is
N=101 circles.
Initial viscosity according to designed electromagnetic coil number of turn N=101 circle, maximum controlling current, damper structure parameter, magnetic rheological liquid special parameter and magnetic rheological liquid is 0.8Pa.s, utilize the 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 auto 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; The 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 namely the piston bore internal diameter is
D H=28mm, diameter of piston rod
d g=18mm, piston length
L=40mm; Annular space between piston and the cylinder barrel
h=0.8mm; The vibration damper top speed
V Max=1.0m/s; The initial viscosity of magnetic rheological liquid is 0.8Pa.s, mangneto shearing stress coefficient
=0.0015, the magnetic intensity index
=1.6; The 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) definite semi-active suspension optimum damping ratio based on travelling comfort
:
Suspension sprung weight according to 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) definite semi-active suspension optimum damping ratio based on Security
:
Sprung weight according to 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:
(3) determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
F IMax
:
Sprung weight according to single-wheel 1/4 vehicle
m 2=350kg, suspension rate
k 2=16719N/m, the suspension lever ratio
I=0.9, the vibration damper setting angle
θ=10 °, the vibration damper top speed
V Max=1.0m/s, in the 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:
(4) the automobile magnetic current semi-active suspension electromagnetic coil number of turn
NOptimal design:
Diameter according to the magneto-rheological vibration damper piston bore
D H=28mm, the annular space between piston and the cylinder barrel
h=0.8mm, piston length
L=40mm, diameter of piston rod
d g=18mm, the mangneto shearing stress coefficient of magnetic rheological liquid
=0.0015, the magnetic intensity index
=1.6, the electromagnetic coil maximum controlling current
I Max=2.0A, and in the step (3)
F Imax=2040.5N is to the number of turn of this auto magnetorheological semi-active suspension electromagnetic coil
NBe optimized design, that is:
Right
NCarry out rounding, optimal design value that can this auto 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 the 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, Zui Da 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; The 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 the cylinder barrel
h=0.7mm; The vibration damper top speed
V Max=1.0m/s; The initial viscosity of magnetic rheological liquid is 0.8Pa.s, mangneto shearing stress coefficient
=0.0015, the magnetic intensity index
=1.6; The 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) definite semi-active suspension optimum damping ratio based on travelling comfort
:
Suspension sprung weight according to 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) definite semi-active suspension optimum damping ratio based on Security
:
Sprung weight according to 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:
(3) determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
F IMax
:
Sprung weight according to single-wheel 1/4 vehicle
m 2=400kg, suspension rate
k 2=20884N/m, the suspension lever ratio
I=0.9, the vibration damper setting angle
θ=10 °, the vibration damper top speed
V Max=1.0m/s, in the 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:
Diameter according to the magneto-rheological vibration damper piston bore
D H=28mm, the annular space between piston and the cylinder barrel
h=0.7mm, piston length
L=40mm, diameter of piston rod
d g=20mm, the mangneto shearing stress coefficient of magnetic rheological liquid
=0.0015, the magnetic intensity index of mangneto shearing stress
=1.6, the electromagnetic coil maximum controlling current
I Max=2.0A, and in the step (3)
F Imax=1800.4N is to the number of turn of this auto magnetorheological semi-active suspension electromagnetic coil
NBe optimized design, that is:
Right
NCarry out rounding, optimal design value that can this auto 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 the 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, Zui Da 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; The 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 the cylinder barrel
h=0.7mm; The vibration damper top speed
V Max=1.0m/s; The mangneto shearing stress coefficient of magnetic rheological liquid
=0.002, the magnetic intensity index
=1.5; The 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) definite 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, desired semi-active suspension optimum damping ratio based on travelling comfort
Also identical with embodiment three, that is:
(2) definite semi-active suspension optimum damping ratio based on Security
:
Because the single-wheel suspension parameter of this automobile is identical with embodiment three, therefore, desired semi-active suspension optimum damping ratio based on Security
Also identical with embodiment three, that is:
(3) determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
F IMax
:
Sprung weight according to single-wheel 1/4 vehicle
m 2=400kg, suspension rate
k 2=20884N/m, the suspension lever ratio
I=0.95, the vibration damper setting angle
θ=8 °, the vibration damper top speed
V Max=1.0m/s, in the 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:
(4) the automobile magnetic current semi-active suspension electromagnetic coil number of turn
NOptimal design:
Diameter according to the magneto-rheological vibration damper piston bore
D H=28mm, the annular space between piston and the cylinder barrel
h=0.7mm, piston length
L=40mm, diameter of piston rod
d g=18mm, the mangneto shearing stress coefficient of magnetic rheological liquid
=0.002, the magnetic intensity index of mangneto shearing stress
=1.5, the electromagnetic coil maximum controlling current
I Max=2.0A, and in the step (3)
F Imax=1598.1N is to the number of turn of this auto magnetorheological semi-active suspension electromagnetic coil
NBe optimized design, that is:
Right
NCarry out rounding, optimal design value that can this auto 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, mangneto shearing stress coefficient
=0.002, the magnetic intensity index
=1.5; Utilize the 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 auto magnetorheological semi-active suspension electromagnetic coil number of turn is correct, reliable.
Claims (4)
1. the design method of the auto magnetorheological semi-active suspension electromagnetic coil number of turn, its concrete calculation procedure is as follows:
(1) definite semi-active suspension optimum damping ratio based on travelling comfort
:
Suspension sprung weight according to 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) definite semi-active suspension optimum damping ratio based on Security
:
Suspension sprung weight according to 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
:
Suspension sprung weight according to single-wheel 1/4 vehicle
m 2, suspension rate
k 2, the suspension lever ratio
i, the vibration damper setting angle
θ, the vibration damper top speed
V Max, in the step (1)
And in the 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:
Diameter according to the magneto-rheological vibration damper piston bore
D H, the annular space between piston and the cylinder barrel
h, piston length
L, diameter of piston rod
d g, the mangneto shearing stress coefficient of magnetic rheological liquid
And magnetic intensity index
, the electromagnetic coil maximum controlling current
I Max, and in the step (3)
F Imax, to the number of turn of auto magnetorheological semi-active suspension electromagnetic coil
NBe optimized design, that is:
2. according to the step (1) in the described method of claim 1 and step (2), it is characterized in that: 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 respectively
With the optimum damping ratio based on Security
, that is:
3. according to the step (3) in the described method of claim 1, it is characterized in that: according to suspension parameter, the vibration damper top speed of single-wheel 1/4 vehicle
V Max, semi-active suspension is based on the optimum damping ratio of travelling comfort
With the optimum damping ratio based on Security
, determine the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
F IMax
, that is:
4. according to the step (4) in the described method of claim 1, it is characterized in that: according to the needed maximum Coulomb damping power of semi-active suspension magneto-rheological vibration damper
F IMax
, the structural parameter of magneto-rheological vibration damper, the special parameter of magnetic rheological liquid, the maximum controlling current of electromagnetic coil
I Max, to the number of turn of auto magnetorheological semi-active suspension electromagnetic coil
NBe optimized design, that is:
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| Application Number | Priority Date | Filing Date | Title |
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| CN201310212217.4A CN103244600B (en) | 2013-05-31 | 2013-05-31 | Design method of turn number of electromagnetic coil of automotive magneto-rheological semi-active suspension |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201310212217.4A CN103244600B (en) | 2013-05-31 | 2013-05-31 | Design method of turn number of electromagnetic coil of automotive magneto-rheological semi-active suspension |
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| CN103244600B CN103244600B (en) | 2014-12-03 |
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| CN201310212217.4A Expired - Fee Related CN103244600B (en) | 2013-05-31 | 2013-05-31 | Design method of turn number of electromagnetic coil of automotive magneto-rheological semi-active suspension |
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| CN111002764A (en) * | 2018-10-06 | 2020-04-14 | 冯艳 | Magnetic fluid rigidity-adjustable tire |
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| US20050080459A1 (en) * | 2003-10-09 | 2005-04-14 | Jacobson Jerry I. | Cardioelectromagnetic treatment |
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| CN111002764A (en) * | 2018-10-06 | 2020-04-14 | 冯艳 | Magnetic fluid rigidity-adjustable tire |
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