CN103174789A - Designing method of magneto-rheological absorber damping channel width based on characteristic requirements - Google Patents
Designing method of magneto-rheological absorber damping channel width based on characteristic requirements Download PDFInfo
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- CN103174789A CN103174789A CN201310113166XA CN201310113166A CN103174789A CN 103174789 A CN103174789 A CN 103174789A CN 201310113166X A CN201310113166X A CN 201310113166XA CN 201310113166 A CN201310113166 A CN 201310113166A CN 103174789 A CN103174789 A CN 103174789A
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Abstract
The invention relates to a designing method of magneto-rheological absorber damping channel width based on characteristic requirements and belongs to the technical field of absorbers. At present, a reliable designing method of the magneto-rheological absorber annular damping channel width is not available neither in China nor abroad, and the width is obtained by choosing a design value from a design range by experience in most cases, and therefore a reliable design parameter is hard to obtain and smooth operation of a vehicle can not be guaranteed in a power off situation. The designing method of the magneto-rheological absorber damping channel width based on the characteristic requirements is characterized in that the damping channel width h is designed optimally according to the magneto-rheological absorber damping characteristic requirements, the inner diameter DH of a piston cylinder, the diameter dg of a piston rod, length L of a piston and magneto-rheological liquid initial viscosity mu 0. The damping channel width h designed with the method is reliable, magneto-rheological absorber damping characteristics are enabled to be optimized, the smooth operation of the vehicle is ensured in the power off situation, the rate of product development is improved, test cost is reduced, product designing level is improved, and product quality and product properties are improved.
Description
Technical field
The present invention relates to magneto-rheological vibration damper, particularly based on the design method of the magneto-rheological vibration damper damp channel width of characteristic requirements.
Background technique
Magneto-rheological vibration damper can be realized by the size of controlling electric current the control to absorber damping force, it has fast response time, low in energy consumption, the characteristics such as regulation range is large, and operating conditions is relatively simple, a focus of Present Domestic, outer automotive suspension research field.The annular damp channel width of magneto-rheological vibration damper
hBe the important feature parameter of magneto-rheological vibration damper, determining the flow damping characteristic of vibration damper, automobile ride is had material impact.Magneto-rheological vibration damper damp channel width
hThe parameter designing value, should control under current conditions not applying, its damping characteristic still can also satisfy the basic demand of automobile ride.Yet, according to consult reference materials, at present the home and abroad is for magneto-rheological vibration damper damp channel width
hThis key parameter not yet provides accurate, reliable design method always, is mostly (to select a damp channel width in 1.0 ~ 2.0mm) a scope by rule of thumb
hParameter value, the method for then passing through repetition test, checking and modification is finally determined this magneto-rheological vibration damper damp channel width
hThe actual design value.Along with the fast development of automotive industry and improving constantly of Vehicle Speed, design to magneto-rheological vibration damper is had higher requirement, therefore, must set up the design method of a kind of accurate, reliable magneto-rheological vibration damper damp channel width h, to satisfy and the accurately requirement of design quick to magneto-rheological vibration damper, reduce design and testing expenses and maintenance expenses, improve designing quality, level and the performance of magneto-rheological vibration damper, improve the run smoothness of vehicle.
Summary of the invention
For the defective that exists in above-mentioned prior art, technical problem to be solved by this invention be to provide a kind of accurately, reliably based on the design method of the magneto-rheological vibration damper damp channel width of characteristic requirements, its design cycle is as shown in Figure 1.
In order to solve the problems of the technologies described above, the design method of the magneto-rheological vibration damper damp channel width based on characteristic requirements provided by the present invention, its technological scheme implementation step is as follows:
(1) determine the magneto-rheological vibration damper operating rate
V
1
And the corresponding damping force that requires
F
1
:
Do not applying the control electric current according to magneto-rheological vibration damper
IThe desired damping force characteristic curve of design in situation is determined the routine work speed of vibration damper
V 1Point and corresponding desired damping force
F 1
(2) magneto-rheological vibration damper damp channel width
hMathematical optimization models and design:
According to the internal diameter of the piston bore of magneto-rheological vibration damper be
D H, piston length
L, the diameter of piston rod is
d g, the initial viscosity of magnetic rheological liquid
μ 0, in step (1)
V 1With
F 1, utilize movement velocity, flow, choke pressure and the absorber damping force Relations Among of magneto-rheological vibration damper, set up magneto-rheological vibration damper damp channel width
hThe design mathematic model, that is:
In formula,
;
Namely
Wherein,
,
,
,
,
Separate above-mentioned about
h4 equation of n th order n, just can obtain getting magneto-rheological vibration damper damp channel width
hDesign load;
(3) simulating, verifying of magneto-rheological vibration damper damping characteristic:
Piston bore internal diameter according to magneto-rheological vibration damper
D H, diameter of piston rod
d g, and designed damp channel width in step (2)
h, utilize magneto-rheological vibration damper damping characteristic simulated program, the damping characteristic of designed magneto-rheological vibration damper when not applying the control electric current carried out simulating, verifying.
The present invention has advantages of than prior art:
At present the home and abroad not yet provides reliable design method for the annular damp channel width of magneto-rheological vibration damper, is mostly by rule of thumb at general scope (damp channel width of selection in 1.0mm ~ 2.0mm)
hDesign load, the method for then passing through repetition test, checking and modification is finally determined the actual design value of this design magneto-rheological vibration damper damp channel width.Therefore, traditional design method can not guarantee that the damping characteristic of magneto-rheological vibration damper reaches best, even can not satisfy the basic demand of vehicle running smoothness at all under powering-off state.The present invention is according to the piston bore internal diameter of magneto-rheological vibration damper
D H, diameter of piston rod
d g, magnetic rheological liquid initial viscosity
μ 0, the resistance of shock absorber characteristic designing requirement, to magneto-rheological vibration damper damp channel width
hBe optimized design.Utilize the method, can obtain reliable magneto-rheological vibration damper damp channel width
hThe parameter designing value, can make the damping characteristic of magneto-rheological vibration damper reach best, but also can satisfy at the prime design requirement of the in particular cases automobile ride that cuts off the power supply to the resistance of shock absorber characteristic, simultaneously, utilize this design method can accelerate product development speed, reduce design and testing expenses, improve design level, the quality and performance of magneto-rheological vibration damper, improve vehicle running smoothness, and at magneto-rheological vibration damper in outage in particular cases, still guarantee the driving safety of automobile.
Be further described below in conjunction with accompanying drawing in order to understand better the present invention.
Fig. 1 is magneto-rheological vibration damper damp channel width
hDesign flow diagram;
Fig. 2 is the schematic diagram of magneto-rheological vibration damper piston bore and piston and damp channel;
Fig. 3 is that embodiment one magneto-rheological vibration damper does not add and designs desired damping characteristic curve when controlling electric current;
Fig. 4 is embodiment one the damping characteristic simulation curve of design magneto-rheological vibration damper when not adding the control electric current;
Fig. 5 is that embodiment two magneto-rheological vibration damper does not add and designs desired damping characteristic curve when controlling electric current;
Fig. 6 is embodiment two the damping characteristic simulation curve of design magneto-rheological vibration damper when not adding the control electric current.
Fig. 7 is that embodiment three magneto-rheological vibration damper does not add and designs desired damping characteristic curve when controlling electric current;
Fig. 8 is embodiment three the damping characteristic simulation curve of design magneto-rheological vibration damper when not adding the control electric current.
Specific embodiments
Below by embodiment, the present invention is described in further detail.
Embodiment one: the schematic diagram of certain auto magnetorheological damper piston cylinder barrel and piston and damp channel, as shown in Figure 2, 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, the annular space between the inwall of piston 2 and piston bore 1
h, be the width of magneto-rheological vibration damper damp channel
hThe internal diameter of the piston bore of this magneto-rheological vibration damper is
D H=28mm, diameter of piston rod
d g=18mm, piston length
L=40mm; The initial viscosity of magnetic rheological liquid is not 0.8Pa.s during externally-applied magnetic field, and magneto-rheological vibration damper is not applying the control electric current
IIn situation, design desired damping force characteristic curve, as shown in Figure 3, to the damp channel width of this magneto-rheological vibration damper
hDesign.
The design method based on the magneto-rheological vibration damper damp channel width of characteristic requirements that example of the present invention provides, its design cycle as shown in Figure 1, concrete steps are as follows:
(1) determine the magneto-rheological vibration damper operating rate
V
1
And corresponding desired damping force
F
1
:
Do not applying the control electric current according to magneto-rheological vibration damper
IIn situation, design desired damping force characteristic curve, as shown in Figure 3, determine the operating rate of vibration damper
V 1=0.3m/s, and corresponding desired damping force
F 1=300N;
(2) magneto-rheological vibration damper damp channel width
hMathematical optimization models and design:
According to the internal diameter of the piston bore of magneto-rheological vibration damper be
D H=28mm, the diameter of piston rod is
d g=18mm, the initial viscosity of magnetic rheological liquid
μ 0=0.8Pa.s, piston length
L=40mm, and in step (1)
V 1=0.3m/s and
F 1=300N utilizes magneto-rheological vibration damper speed, flow, choke pressure and damping force Relations Among, sets up magneto-rheological vibration damper damp channel width
hThe design mathematic model, that is:
In formula,
=1.3263 * 10
4;
Namely
Wherein,
=1.3279 * 10
4,
=-371.81,
=0.0068,
=-5.1520 * 10
-5,
=2.116 * 10
-7,
Separate above-mentioned about
h4 equation of n th order n, just can obtain this magneto-rheological vibration damper damp channel width
hDesign load, that is:
h=0.0008m＝0.8mm；
(3) simulating, verifying of magneto-rheological vibration damper damping characteristic:
Piston bore internal diameter according to magneto-rheological vibration damper
D H=28mm, diameter of piston rod
d g=18mm, the kinetic viscosity of magnetic flow liquid
μ 0=0.8Pa.s, and in step (2)
h=0.8mm utilizes magneto-rheological vibration damper damping characteristic simulated program, and the damping characteristic of designed magneto-rheological vibration damper is carried out simulating, verifying, the resulting damping characteristic curve of emulation, as shown in Figure 4.
According to simulation results Fig. 4 as can be known, this magneto-rheological vibration damper do not add when controlling electric current
V 1The damping force at speed point place
F 1, desired damping characteristic curve Fig. 3 matches with design, shows this magneto-rheological vibration damper damp channel width
hMeter
The value of establishing be reliably, the magneto-rheological vibration damper damp channel width of setting up
hDesign method be correct.
Embodiment two: the structural parameter of certain auto magnetorheological vibration damper 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.The initial viscosity of magnetic rheological liquid and the requirement of resistance of shock absorber characteristics design are not identical with embodiment's one, and wherein, the initial viscosity of magnetic rheological liquid is 0.7Pa.s, and magneto-rheological vibration damper is not applying the control electric current
IIn situation, design desired damping force characteristic curve, as shown in Figure 5, to this magneto-rheological vibration damper damp channel width
hDesign.
Adopt embodiment one design procedure, to the damp channel width of magneto-rheological vibration damper
hDesign:
(1) determine the magneto-rheological vibration damper operating rate
V
1
And corresponding desired damping force
F
1
:
Do not applying the control electric current according to magneto-rheological vibration damper
IIn situation, design desired damping force characteristic curve, as shown in Figure 5, determine the operating rate of vibration damper
V 1=0.3m/s, and corresponding desired damping force
F 1=350N;
(2) set up the damp channel width of magneto-rheological vibration damper
hThe design mathematic model:
According to the internal diameter of the piston bore of magneto-rheological vibration damper be
D H=28mm, the diameter of piston rod is
d g=18mm, the initial viscosity of magnetic rheological liquid
μ 0=0.7Pa.s, piston length
L=40mm, and in step (1)
V 1=0.3m/s and
F 1=350N utilizes magneto-rheological vibration damper speed, flow, choke pressure and damping force Relations Among, sets up magneto-rheological vibration damper damp channel width
hThe design mathematic model, that is:
In formula,
=1.7684 * 10
4;
Namely
Wherein, wherein,
=1.77 * 10
4,
=-495.6,
=0.0068,
=-5.1520 * 10
-5,
=2.116 * 10
-7
Separate above-mentioned about
h4 equation of n th order n, just can obtain this magneto-rheological vibration damper damp channel width
hDesign load, that is:
h=0.0007m＝0.7mm；
(3) simulating, verifying of magneto-rheological vibration damper damping characteristic:
Piston bore internal diameter according to magneto-rheological vibration damper
D H=28mm, diameter of piston rod
d g=18mm, the initial viscosity of magnetic rheological liquid
μ 0=0.7Pa.s, and designed damp channel width in step (2)
h=0.7mm utilizes magneto-rheological vibration damper damping characteristic simulated program, and the damping characteristic when not applying the control electric current of designed magneto-rheological vibration damper is carried out emulation, resulting damping characteristic simulation curve, as shown in Figure 6.
According to damping characteristic simulation results Fig. 6 as can be known, this magneto-rheological vibration damper do not add when controlling electric current
V 1The damping force at speed point place
F 1, desired damping characteristic curve Fig. 5 matches with design, shows this magneto-rheological vibration damper damp channel width
hThe design design load be reliable.
Embodiment three: the piston bore internal diameter of certain auto magnetorheological vibration damper is
D H=28mm, diameter of piston rod
d g=18mm, piston length
L=50mm, the initial viscosity of magnetic rheological liquid are 0.9Pa.s, and magneto-rheological vibration damper is not applying the control electric current
IIn situation, design desired damping force characteristic curve, as shown in Figure 7, to this magneto-rheological vibration damper damp channel width
hDesign.
Adopt embodiment one design procedure, to the damp channel width of magneto-rheological vibration damper
hDesign:
(1) determine the magneto-rheological vibration damper operating rate
V
1
And corresponding desired damping force
F
1
:
Do not applying the control electric current according to magneto-rheological vibration damper
IIn situation, design desired damping force characteristic curve, as shown in Figure 7, determine the operating rate of vibration damper
V 1=0.3m/s, and corresponding desired damping force
F 1=220N;
(2) set up the damp channel width of magneto-rheological vibration damper
hThe design mathematic model:
According to the internal diameter of the piston bore of magneto-rheological vibration damper be
D H=28mm, the diameter of piston rod is
d g=18mm, the initial viscosity of magnetic rheological liquid
μ 0=0.9Pa.s, piston length
L=50mm, and in step (1)
V 1=0.3m/s and
F 1=220N utilizes magneto-rheological vibration damper speed, flow, choke pressure and damping force Relations Among, sets up magneto-rheological vibration damper damp channel width
hThe design mathematic model, that is:
In formula,
=6.9164 * 10
3;
Namely
Wherein,
=6.9324 * 10
3,
=-194.1,
=0.0068,
=-5.1520 * 10
-5,
=2.116 * 10
-7
Separate above-mentioned about
h4 equation of n th order n, just can obtain this magneto-rheological vibration damper damp channel width
hDesign load, that is:
h=0.001m＝1.0mm；
(3) simulating, verifying of magneto-rheological vibration damper damping characteristic:
Piston bore internal diameter according to magneto-rheological vibration damper
D H=28mm, diameter of piston rod
d g=18mm, the initial viscosity of magnetic rheological liquid
μ 0=0.9Pa.s, and designed damp channel width in step (2)
h=1.0mm utilizes magneto-rheological vibration damper damping characteristic simulated program, and the damping characteristic when not applying the control electric current of designed magneto-rheological vibration damper is carried out emulation, resulting damping characteristic simulation curve, as shown in Figure 8.
According to damping characteristic simulation results Fig. 8 as can be known, this magneto-rheological vibration damper do not add when controlling electric current
V 1The damping force at speed point place
F 1, desired damping characteristic curve Fig. 7 matches with design, shows this magneto-rheological vibration damper damp channel width
hDesign load be reliably, this magneto-rheological vibration damper damp channel width
hDesign method be correct.
Claims (2)
1. based on the design method of the magneto-rheological vibration damper damp channel width of characteristic requirements, its concrete steps are as follows:
(1) determine the magneto-rheological vibration damper operating rate
V
1
And the corresponding damping force that requires
F
1
:
Do not applying the control electric current according to magneto-rheological vibration damper
IThe desired damping force characteristic curve of design in situation is determined the routine work speed of vibration damper
V 1Point and corresponding desired damping force
F 1
(2) magneto-rheological vibration damper damp channel width
hMathematical optimization models and design:
According to the internal diameter of the piston bore of magneto-rheological vibration damper be
D H, piston length
L, the diameter of piston rod is
d g, the initial viscosity of magnetic rheological liquid
μ 0, in step (1)
V 1With
F 1, utilize movement velocity, flow, choke pressure and the absorber damping force Relations Among of magneto-rheological vibration damper, set up magneto-rheological vibration damper damp channel width
hThe design mathematic model, that is:
In formula,
;
Namely
Wherein,
,
,
,
,
Separate above-mentioned about
h4 equation of n th order n, just can obtain getting magneto-rheological vibration damper damp channel width
hDesign load;
(3) simulating, verifying of magneto-rheological vibration damper damping characteristic:
Piston bore internal diameter according to magneto-rheological vibration damper
D H, diameter of piston rod
d g, and designed damp channel width in step (2)
h, utilize magneto-rheological vibration damper damping characteristic simulated program, the damping characteristic of designed magneto-rheological vibration damper when not applying the control electric current carried out simulating, verifying.
2. the step (2) in method according to claim 1 is characterized in that: according to the internal diameter of the piston bore of magneto-rheological vibration damper be
D H, the gap of establishing between piston and internal diameter of cylinder is
h, piston length
L, the diameter of piston rod is
d g, the initial viscosity of magnetic rheological liquid
μ 0, in step (1)
V 1With
F 1, utilize movement velocity, flow, choke pressure and the absorber damping force Relations Among of magneto-rheological vibration damper, set up magneto-rheological vibration damper damp channel width
hThe design mathematic model, and to the damp channel width
hDesign, namely
In formula,
;
Namely
Wherein,
,
,
,
,
Separate above-mentioned about
h4 equation of n th order n, just can obtain getting magneto-rheological vibration damper damp channel width
hDesign load.
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| CN104595411A (en) * | 2013-10-31 | 2015-05-06 | Dt瑞士公司 | Shock absorption device for bicycle and operation method of shock absorption device |
| CN107654562A (en) * | 2017-11-13 | 2018-02-02 | 武汉理工大学 | A kind of magnetic rheological liquid damper for increasing resistance function with dead electricity |
| WO2023193286A1 (en) * | 2022-04-07 | 2023-10-12 | 深圳市朝上科技有限责任公司 | Magnetorheological damper composed of stepped piston cylinder |
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Cited By (4)
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| CN107654562A (en) * | 2017-11-13 | 2018-02-02 | 武汉理工大学 | A kind of magnetic rheological liquid damper for increasing resistance function with dead electricity |
| WO2023193286A1 (en) * | 2022-04-07 | 2023-10-12 | 深圳市朝上科技有限责任公司 | Magnetorheological damper composed of stepped piston cylinder |
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