CN105818627B - The method that independent suspension equivalent stiffness characteristic is realized using cam curve - Google Patents
The method that independent suspension equivalent stiffness characteristic is realized using cam curve Download PDFInfo
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- CN105818627B CN105818627B CN201610222852.4A CN201610222852A CN105818627B CN 105818627 B CN105818627 B CN 105818627B CN 201610222852 A CN201610222852 A CN 201610222852A CN 105818627 B CN105818627 B CN 105818627B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G3/00—Resilient suspensions for a single wheel
- B60G3/18—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/021—Spring characteristics, e.g. mechanical springs and mechanical adjusting means the mechanical spring being a coil spring
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2200/00—Indexing codes relating to suspension types
- B60G2200/10—Independent suspensions
- B60G2200/14—Independent suspensions with lateral arms
- B60G2200/144—Independent suspensions with lateral arms with two lateral arms forming a parallelogram
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- Vehicle Body Suspensions (AREA)
Abstract
The present invention discloses a kind of method that independent suspension equivalent stiffness characteristic is realized using cam curve, and the damping shock absorber of suspension and push rod is integrated, and the upper end of integrated damper push rod assembly is connected by rubber absorbers with vehicle frame；Lower end is connected by module with the transverse arm of suspension, realized on spring by the molded line for designing module/unsprung mass relative displacement and amount of spring compression meet specific relationship so that the equivalent stiffness of suspension system is definite value.The functional relation between the parameters such as cam profile curve and transverse arm corner, pressure angle, damper angle of inclination is established using reversal process, is programmed using matlab, solution is iterated to the molded line of module, obtain the pitch curve and cam profile of module.By rationally designing the molded line of cam curve, the equivalent stiffness nonlinear characteristic being led to by suspension guide mechanism design is eliminated.The present invention can be applied to arbitrary independent suspension guiding mechanism in principle.
Description
Technical field
The present invention relates to automotive field, in particular to automobile chassis and drive technology field, and in particular to employ
The independent suspension of cam mechanism type vibration absorber, such as wishbone-type independent suspension.
Background technology
That vehicle suspension is broadly divided into is passive, half actively and Active suspension.Semi-active suspension structure is relatively easy, and cost is opposite
It is relatively low, can suspension property be improved according to road surface and speed variation adjustment suspension damping parameter to a certain extent.Active suspension energy
According to road surface and speed variation adjustment suspension active force, essence is equal to the rigidity and damping parameter of adjustment suspension in real time, energy
Utmostly improve suspension property, but because complicated, energy consumption and cost are higher, and application and popularization are by very big restriction.
Although the optimal performance of passive suspension is usually compromised by certain specific road surface and velocity conditions, due to structure letter
Single, cost is relatively low, and passive suspension is still widely used on automobile.Passive suspension is divided into for rigid axle suspension and independently outstanding
Frame.Wherein, rigid axle suspension is mainly used in lorry, and car then mainly uses independent suspension.Equip the vehicle of independent suspension
Both sides wheel is beated independently of each other in certain amount of deflection, can be weakened vehicle body and frame weaving, be improved ride comfort；The opposing party
Face, most of parts of transmission system are arranged on vehicle body, can reduce nonspring carried mass, and the impact that suspension is subject to reduces,
The ride comfort of vehicle body can be improved；Independent suspension is also possible that vehicle body barycenter declines, and improves Riding Stability of Automobile.It is comprehensive
Most of the various advantages of independent suspension, the design of Hyundai Motor drive and transmission system are all based on carrying out on the basis of independent suspension
's.
According to different demands, independent suspension has derived many forms, as independent suspension by swinging arms, trailing arm type independently hang
Frame, mopherson type suspention, single oblique arm type independent suspension etc..It is however non-thread all there are structure in all suspension frame structures
Property the problem of, i.e., in the decrement and spring of bearing spring/gearratio of unsprung mass relative displacement is with suspension bounce position
It is different and change, and on spring/unsprung mass speed of related movement keep constant when, the stretching speed of damper is not permanent
It is fixed, it changes so as to cause suspension system equivalent stiffness and equivalent damping.
In the design of passive suspension, the tradeoff of suspension is optimal in specific road surface and operating mode, parameter one
Denier determines just not change, therefore usually using the equivalent stiffness of equilbrium position and equivalent damping as design considerations.Pass through adjusting
The rigidity and damping characteristic of suspension so that the Frequency Response that vehicle body is responded between the excitation of ground meets certain requirements.Such as resonance
Frequency should avoid that human body sensitive range, resonance peak are as small as possible, tyre dynamic load should meet security requirement, suspension moves stroke
It is less than the limit travel of suspension to reduce probability of suspension shock limited block etc..However, since suspension system is non-in the presence of moving
Linear characteristic, it is not excellent enough that traditional design method is likely to cause suspension property, such as due to resistance of shock absorber characteristic curve
With the body vibrations under unevenness road surface big caused by bad are big, noise is big；Under Excitation of Random Road Surface, with the increasing of unevenness
Add, vehicle body acceleration amplification factor peak of curve becomes larger and past high-frequency mobile, will if crest frequency is in human body sensitive range
Influence comfort of vehicle etc..Consider the kinematic nonlinearities of suspension system, equivalent stiffness is variation, i.e. equivalent spring is non-for one
Hookean spring.By nonlinear spring analysis by Linearization it is found that suspension equivalent stiffness is directly proportional to camber of spring virtual value square, then
Increased in unevenness and speed, nonlinear spring will cause the degree that comfort declines to be more than ideal linearity spring,
Tyre dynamic load variation can become larger in resonance region.In summary analyze, it is desirable to passive suspension equivalent stiffness and equivalent damping it is non-
Linear factor is preferably minimized, and improves ride comfort and the safety of suspension.
Invention content
The present invention provides a kind of structures and methods that independent suspension equivalent stiffness characteristic is realized using cam curve.
The technical scheme is that：
Design a kind of double cross arm independent suspension of combination cam mechanism type vibration absorber, including the first elastic hinge, Top Crossbeam,
First flexural pivot, knuckle, the second flexural pivot, lower cross arm, the second elastic hinge, vehicle frame, rubber absorbers, integrated damper-push rod
Assembly, bearing spring, module, roller, Roller Shaft, Top Crossbeam are connected by the first elasticity hinge with vehicle frame, and lower cross arm passes through
Second elasticity hinge is connected with vehicle frame；Top Crossbeam is connected by the first flexural pivot with knuckle, and lower cross arm is by the second flexural pivot with turning to
Section is connected；The upper end of integrated damper-push rod assembly is connected firmly by rubber absorbers and vehicle frame, the axis and vehicle frame of damper
It is relatively fixed；The lower end of integrated damper-push rod assembly is connected by Roller Shaft with roller, and roller can be in module
It is rolled along cam profile, module is connected firmly by screw and lower cross arm.
The method that independent suspension equivalent stiffness feature structure is realized using cam curve, is included the following steps：
1）By designing the molded line of module ,/variable quantity and length of unsprung mass relative displacement are realized on spring
Variable quantity meet specific relationship so that the equivalent stiffness of suspension system be definite value；
Equivalent stiffness under the particular kind of relationship,Rigidity for bearing spring；
2）Cam profile curve is established using reversal process and transverse arm corner, pressure angle, integrated damper-push rod assembly are oblique
The functional relation between angle parameter is put, is programmed using matlab, solution is iterated to the molded line of module；
3）The equivalent stiffness according to step 1 substitutes into torque equilibrium equation, obtains on spring/unsprung mass relative displacement
With amount of spring compression needed for the relationship that meets, with reference to cam curve principle of coordinate transformation, pressure angle approximate formula, by
Matlab iterative programs obtain cam profile；
Compared with prior art, superior efficacy of the invention is：
（1）Using the designability of cam curve, realize the characteristic of independent suspension ideal equivalent stiffness, can be applied in principle
In arbitrary independent suspension guiding mechanism；
（2）The transverse arm of integrated damper-push rod assembly and suspension is connected by module, so as to so that on spring/
Meet formula between the variable quantity of unsprung mass relative displacement and corresponding amount of spring compression（4）Relationship, eliminate suspension frame structure it is non-
The adverse effect that linear factor is brought to performances such as ride performance and safeties；
（3）The Profile Design of module is flexible, can realize the different equivalent stiffness of suspension system by changing molded line, be
Suspension design provides facility；
（4）Suspension bodies structure does not need to redesign, and module is compact-sized, occupies little space, and module
It is easy to remove and repair, reduces cost.
Description of the drawings
Fig. 1 is Design of cam curves schematic diagram of the present invention
Fig. 2 is the double cross arm independent suspension structural scheme of mechanism with reference to cam mechanism type vibration absorber
Fig. 3 is lower cross arm corner-wheel side displacement curve
Fig. 4 is cam reason profile and cam profile
Fig. 5 is that cam profile respectively presses angle-lower cross arm rotation curve
Fig. 6 is cam verification curve
Figure label explanation：
1 --- vehicle frame；2 --- Top Crossbeam；
3 --- knuckle；4 --- lower cross arm；
5 --- rubber absorbers；
501 --- vibration isolation rubber block；502 --- damper connector；
6 --- integrated damper-push rod assembly；
7 --- bearing spring；8 --- module；
9 --- roller；10 --- Roller Shaft；
I --- the first elasticity hinge；II --- the second elasticity hinge；
II --- the first flexural pivot；IV --- the second flexural pivot.
Specific embodiment
The present invention is integrated by the damping shock absorber of suspension and push rod, the upper end of integrated damper-push rod assembly
It is connected by rubber absorbers with vehicle frame, lower end is connected by module with the transverse arm of suspension, by designing module
Molded line realized on spring/unsprung mass relative displacement and spring deflection meet specific relationship so that suspension system it is equivalent just
It spends for definite value.The functional relation between the parameters such as cam profile curve and transverse arm corner, pressure angle is established using reversal process, is used in combination
Matlab is programmed, and solution is iterated to the molded line of module.
By rationally designing the molded line of cam curve, realize the characteristic of independent suspension ideal equivalent stiffness, eliminate suspension fortune
The non-linear harmful effect brought to ride performance and safety etc. is moved, arbitrary independent suspension Guiding machine is can be applied in principle
Structure.
The structures and methods of independent suspension ideal equivalent stiffness characteristic are realized using cam curve, can be applied to appoint in principle
Meaning independent suspension guiding mechanism.
The present invention is using double cross arm independent suspension as specific embodiment.
A kind of double cross arm independent suspension for combining cam mechanism type vibration absorber, including the first elastic hinge, Top Crossbeam, the
One flexural pivot, knuckle, the second flexural pivot, lower cross arm, the second elastic hinge, vehicle frame, rubber absorbers, integrated damper-push rod are total
Into, bearing spring, module, roller, Roller Shaft.Wherein, Top Crossbeam is connected by the first elasticity hinge with vehicle frame, and lower cross arm leads to
The second elasticity hinge is crossed with vehicle frame to be connected.Knuckle is connected by the first flexural pivot and the second flexural pivot with Top Crossbeam, lower cross arm.Integration
Damper-push rod assembly forms the buffer element of suspension system with bearing spring.Wherein, integrated damper-push rod assembly
Upper end is connected firmly by rubber absorbers and vehicle frame, on the one hand so that the axis of damper is relatively fixed with vehicle frame, on the other hand may be used
With the impact of buffering integrated damper-between push rod assembly and vehicle frame；Its lower end is connected by Roller Shaft with roller, Roller Shaft
It connect to rub to reduce by bearing between roller.Roller can roll in module along cam profile, roller surface
Abrasion caused by engineering duroplasts can be used to reduce roller rolls with module inner surface.Module is by screw under
Transverse arm connects firmly.
In vehicle operation, Top Crossbeam and knuckle can be relatively rotated around the first flexural pivot, and Top Crossbeam and vehicle frame can be around
First elasticity hinge relatively rotates；Lower cross arm can be relatively rotated with knuckle around the second flexural pivot, and lower cross arm can be around the second bullet with vehicle frame
Property hinge relatively rotate；The axis relative frame of integrated damper-push rod assembly is fixed, and damper is along axis when being suspended in bounce
It stretches in direction；Bearing spring is mounted between the spring fastening of integrated damper-push rod assembly；Roller passes through Roller Shaft and one
Body damper-push rod assembly is connected, and in Suspension movement, roller is rolled along module molded line.
The design method schematic diagram of cam curve is as shown in Figure 1, wherein roller centre track forms cam curve, integration
Damper-push rod assembly is equivalent to translating follower.The centre of gyration of suspension transverse arm isPoint, when driven member is in position 1, if
The initial position of roller centreStarting point for cam curve.When suspension transverse arm aroundPress rotated counterclockwise by angle（Inverse time
Needle is just）Afterwards, using relativity is moved, be equivalent to driven member aroundPoint rotates clockwise angle, position 2 in Fig. 2 is reached,
WithEqual in magnitude, direction is opposite.Roller centre is reached on cam curvePoint, the movement of roller centre can regard as byPoint is first
AroundDot inversion angleIt reachesIt is moved again along driven member guide rail after pointAfter reachPoint, i.e., in transverse arm rotation angleAfterwards from
Moving part（Integrated damper-push rod assembly）Stroke be。
Using coordinate transform and translation transformation,The coordinate such as formula of point（1）It is shown：
Wherein,For driven member aroundThe reverse angle of point, clockwise for just；Being integrated damper-push rod assembly with
The angle of lower cross arm；、For starting pointCoordinate.
As shown in Figure 1, the offset or dish that integrated damper-push rod assembly relatively rotates center is, due to its axis phase
Vehicle frame is fixed, thenIt remains unchanged；Ground contact point is with respect to the arm of force at transverse arm rotation center, suspension is during the motion
There are lateral sliding amount, and lateral sliding amount is generally less than 0.5 after suspension structural optimization, relative to the wheel side of suspension
For displacement or amount of spring compression, lateral sliding amount is very small, therefore does not consider lateral sliding amount to the arm of forceThe influence brought.
Ignore the frictional force between cam and roller, can must take turns side power and the equalising torque relationship of spring force：
Wherein,For on spring/variable quantity of unsprung mass relative displacement；It is corresponded to for bearing spring length's
Variable quantity；That is the total deflection of spring；It is corresponded to for bearing spring powerVariable quantity；It is corresponded to for wheel side powerVariable quantity；To take turns side equivalent stiffness；Rigidity for bearing spring；It is arrived for equipoise center of rotation
The intersection point of driven member and cam starting pointDistance；Pressure angle between roller and cam, here authorized pressure angle inverse time
Needle is negative.
According to the design requirement of cam, it should cause suspension system steerage side equivalent stiffness perseverance for definite value, for ease of formula（2）Change
Letter simplifies cam design process, it is assumed that suspension system equivalent stiffness such as formula（3）It is shown：
By formula（3）Bring formula into（2）,/variable quantity and the corresponding spring-compressed of unsprung mass relative displacement are can obtain on spring
Amount should meet formula（4）Relationship：
The pressure angle of cam curve such as formula（5）It is shown：
Wherein,Variable quantity for point-to-point transmission abscissa adjacent on cam curve；For point-to-point transmission adjacent on cam curve
The variable quantity of ordinate.
Simultaneous formula（1）, formula（4）And formula（5）Obtain cam curve asks for equation group such as formula（6）It is shown：
By formula（6）It can be seen that, the unknown quantity solved is needed to have
, therefore, can first determine the starting point of cam curveCoordinate, suspension is obtained by simulation softwares such as ADAMS
Take turns side displacementWith swing arm cornerBetween relationship, finally according to formula（6）Cam curve is iterated by matlab programmings
It solves.It should be noted that the discrete interval of wheel side displacement must be sufficiently small, otherwise according to formula（5）Obtained pressure angle with
Error between reality will increase, and lead to cam curve accuracy decline.
It below will be rightSelection analyzed：
1) cam curve functions is avoided non-mapping relationship occur
It can be obtained by Fig. 1, if,, i.e. formula（1）'sAlways it sets up,
Therefore, if, will occur sameIt is two correspondingSituation.
So that curve is reasonable, whenWhen, the starting point of cam curve should be madeA spacing is biased in vertical direction
From；Or integrated damper-push rod assembly is in tilted layout so that.As can be seen from Figure 1,In vertical direction
The physical significance that biasing or integrated damper-push rod assembly are in tilted layout is so that is suspended in the process of upstream or downstream
In, starting pointIt will not cross in the farthest point that it can be reached on the direction of damper axis.I.e.It should meet：
Obviously, whenWhen,Biasing in vertical direction will be designed to cam and reliability of structure is brought not
Profit influences.And on the one hand lateral rigidity that integrated damper-push rod assembly inclination arrangement will increase suspension, on the other hand also make
Obtain starting pointIt will not cross in the farthest point that it can be reached on the direction of damper axis.Therefore, one should be made
Change damper-push rod assembly and tilt certain angle, andShould be as small as possible, this also installation with practical suspension shock-absorber
It is consistent.It is designed to simplify, increases structural reliability, generally take。
2）Avoid cammed compression angle excessive
For this cam structure, roller is equivalent to be contacted with cam inner surface, therefore the pressure angle of cam curve meets：
Take the pressure angle conduct of suspension equipoiseBasis for selecting, as the above analysis,Compare rationally, therefore, substitute into formula（4）：
The pressure angle of equipoise meets：
I.e. the pressure angle of push rod roller and cam profile equipoise pressure angle withSelection
It is unrelated, work as Suspension Construction ParametersAfter determining, the pressure angle of cam curve initial position is definite value.
By deriving above, the design process of cam profile is as follows：
1) in order to increase the lateral rigidity of suspension, while according to formula（7）Requirement, by integrated damper-push rod assembly
It is in tilted layout, the angle of assembly and swing arm is, then it can obtain,,
Tilting angle cannot be excessive, otherwise will cause offset distanceIt is too small, then suspension rateExcessive, the requirement to spring increases；
2) according to formula（7）Requirement, choose, to simplify the process of design, while increase the reliable of structure
Property, it can use；
3) according to formula（6）, solution is iterated to cam curve by matlab programs；
4) it verifies the accuracy of cam curve, checks whether the pressure angle between cam and roller is less than allowable pressure angle.
Cam mechanism is applied to the link position of push rod and lower cross arm by the present invention, since integrated damper-push rod is total
It reduces by a rotational freedom into the relatively traditional double cross arm independent suspension in upper end, is put down Gu increasing by one at the roller of cam mechanism
Degree of freedom is moved, the rotation of roller opposing rollers axis is isolated degree of freedom, therefore the degree of freedom of entire suspension system is constant, meets suspension
Motion requirement.Non-linear relation between wheel side displacement and amount of spring compression can be eliminated by the molded line for controlling module,
So as to eliminate suspension frame structure design it is non-linear caused by suspension frame structure is non-linear and the harmful effect of suspension property.
As shown in Figure 2, a kind of double cross arm independent suspension for combining cam mechanism type vibration absorber, including vehicle frame 1, on
Transverse arm 2, knuckle 3, lower cross arm 4, rubber absorbers 5, integrated damper-push rod assembly 6, bearing spring 7, module 8,
Roller 9, Roller Shaft 10, vibration isolation rubber block 501, damper connector the 502, first elasticity hinge I, the second elasticity hinge II, the first flexural pivot
III, the second flexural pivot IV.
Top Crossbeam 2 cuts with scissors III by the first elasticity and is connected with vehicle frame 1, and lower cross arm 4 cuts with scissors II and 1 phase of vehicle frame by the second elasticity
Even.Top Crossbeam 2 is connected by the first flexural pivot III with knuckle 3, and lower cross arm 2 is connected by the second flexural pivot IV with knuckle 3.One
The upper end of body damper-push rod assembly 6 is connected firmly by rubber absorbers 5 and vehicle frame 1, on the one hand so that integrated damper-
The axis of push rod assembly 6 is relatively fixed with vehicle frame 1, on the other hand can be with buffering integrated damper-push rod assembly 6 and vehicle frame 1
Between impact；Its lower end is connected by Roller Shaft 10 with roller 9, connects to subtract by bearing between Roller Shaft 10 and roller 9
Small friction, and the axis of Roller Shaft 10 is parallel with the axis of elasticity hinge II so that integrated damper-push rod assembly 6 can be along it
Axis direction stretches.Roller 9 can roll in module 8 along cam profile, 9 surface of roller and 8 inner surface of module
Engineering duroplasts can be used to reduce abrasion caused by roller 9 rolls.Module 8 is connected firmly by screw and lower cross arm 4.
In vehicle operation, Top Crossbeam 2 can be relatively rotated with knuckle 3 around the first flexural pivot III, Top Crossbeam 2 and vehicle
Frame 1 can be relatively rotated around the first elasticity hinge I；Lower cross arm 4 can be relatively rotated with knuckle 3 around the second flexural pivot IV, lower cross arm 4 and vehicle
Frame 1 can be relatively rotated around the second elasticity hinge II；The axis relative frame 1 of integrated damper-push rod assembly 6 is fixed, and is suspended in
Integration damper-push rod assembly 6 stretches in the axial direction during bounce；It is total that bearing spring 7 is mounted on integrated damper-push rod
Into between 6 spring fastening 601, pooling feature is served as when suspension is beated；Roller 9 passes through Roller Shaft 10 and integrated vibration damping
Device-push rod assembly 6 is connected, and in Suspension movement, roller 9 rolls, while roller 9 and 10 phase of Roller Shaft along the molded line of module 8
To rotation.
Cam mechanism is applied to the link position of integrated damper-push rod assembly and lower cross arm by the present invention, passes through control
The molded line of module processed can eliminate the non-linear harmful effect to suspension property of suspension frame structure.
The solution of cam curve is described in detail below with reference to a certain double wishbone suspension.
With the minimum optimization aim of the lateral slippage of tire, double wishbone suspension is optimized with reference to ADAMS/Insight,
The factors such as longitudinal tire stiffness, the variation of stub positional parameter are not considered, i.e. plane where suspension link is perpendicular to the ground.Suspension
Elementary structure parameter is as shown in table 1：
Tire earth point is with respect to lower cross arm center of rotationThe arm of force of point, cam
The ratio that distance of the initial point away from center of rotation accounts for lower cross arm length is 0.85, i.e.,Point coordinate be, the angle of integrated damper-push rod assembly and lower cross arm, then integrally
Change the vertical range of damper-push rod assembly and center of rotation。
Wheel side displacement and the relationship of lower cross arm corner are obtained by the Kinematics Simulation of ADMAS, to cause the calculating of pressure angle
Accurately, the corresponding wheel side displacement of step-length of emulation is taken, take turns side displacement and the pass of lower cross arm corner
System is as shown in Figure 3.
According to formula（6）It writes program and solution is iterated to cam curve each point, obtain pitch curve and practical exterior feature
Line such as Fig. 4, the coordinate of pitch curve each point are as shown in table 2：
The pressure angle of cam profile each point and relationship such as Fig. 5 of lower cross arm corner, the range of allowable pressure angle are generally, it is seen that designed cam meets design requirement.Each structural parameters of suspension are substituted into formula（9）Obtain cam initial pointPlace
Theoretical pressure angle be, it is by Fig. 5 gained cam starting point pressure angles, relative error 0.25%, error
The reason of be that the calculating of pressure angle is acquired by adjacent two point coordinates of cam, computational accuracy is related with the resolution ratio of data point, this
In wheel side displacement per 0.1mm measure iterative data of the data point as cam curve.
According to the specification of above-mentioned cam curve, the variable quantity of variable quantity and length for taking turns side displacement need to meet formula（4）
Requirement, enable, then
, due to the corresponding wheel side displacement of the step-length of ADAMS, then the variable quantity of length should meet formula
（10）Requirement：
The verification curve of cam is as shown in Figure 6, it can be seen that designed cam is met the requirements.
Claims (1)
1. a kind of method that independent suspension equivalent stiffness characteristic is realized using cam curve, is designed a kind of combination cam mechanism type and subtracted
The double cross arm independent suspension of vibrating device, including the first elastic hinge, Top Crossbeam, the first flexural pivot, knuckle, the second flexural pivot, lower cross arm,
Second elastic hinge, vehicle frame, rubber absorbers, integrated damper-push rod assembly, bearing spring, module, roller, roller
Axis, Top Crossbeam are connected by the first elasticity hinge with vehicle frame, and lower cross arm is connected by the second elasticity hinge with vehicle frame；Top Crossbeam passes through
One flexural pivot is connected with knuckle, and lower cross arm is connected by the second flexural pivot with knuckle；The upper end of integrated damper-push rod assembly
It is connected firmly by rubber absorbers and vehicle frame, axis and the vehicle frame of damper are relatively fixed；Under integrated damper-push rod assembly
End is connected by Roller Shaft with roller, and roller can roll in module along cam profile, module by screw and
Lower cross arm connects firmly；The cam profile is designed to include the following steps：
1）By designing the molded line of module ,/the change of the variable quantity and length of unsprung mass relative displacement is realized on spring
Change amount meets specific relationship so that the equivalent stiffness of suspension system is definite value；
Equivalent stiffness under the particular kind of relationship,Rigidity for bearing spring；Being integrated vibration damping
Device-push rod assembly relatively rotates the offset or dish at center；For the arm of force of the ground contact point with respect to transverse arm rotation center；
2）Cam profile curve and transverse arm corner, pressure angle, integrated damper-push rod assembly oblique angle are established using reversal process
The functional relation between parameter is spent, is programmed using matlab, solution is iterated to the molded line of module；
3）The equivalent stiffness according to step 1 is substituted into torque equilibrium equation, obtains on spring/unsprung mass relative displacement and bullet
The relationship met needed for spring decrement, with reference to cam curve principle of coordinate transformation, pressure angle approximate formula, is changed by matlab
Cam profile is obtained for program.
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| CN107884207B (en) * | 2017-11-16 | 2019-08-30 | 徐州工业职业技术学院 | A kind of Independent Suspension fatigue test monitor station |
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| CN112231822B (en) * | 2019-06-28 | 2024-07-12 | 广州汽车集团股份有限公司 | Suspension hard spot analysis method and system and computer readable storage medium |
| CN112800539B (en) * | 2021-01-15 | 2024-06-14 | 中国商用飞机有限责任公司北京民用飞机技术研究中心 | Nail load distribution prediction method and system |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2434129A (en) * | 2004-03-12 | 2007-07-18 | Honda Motor Co Ltd | Suspension device |
| EP2165862A1 (en) * | 2008-09-23 | 2010-03-24 | Audi AG | Device for adjusting a wheel of a wheel suspension |
| CN201685676U (en) * | 2010-01-18 | 2010-12-29 | 简式国际汽车设计（北京）有限公司 | Double transverse arm independent suspension frame |
| CN201914045U (en) * | 2010-12-15 | 2011-08-03 | 陈言平 | Shock-absorber assembly of double-wishbone independent suspension |
| CN203511207U (en) * | 2013-08-15 | 2014-04-02 | 上海通用汽车有限公司 | Double wishbone suspension and vehicle body equipment with double wishbone suspension |
| CN204249767U (en) * | 2014-10-27 | 2015-04-08 | 北奔重型汽车集团有限公司 | A kind of double cross arm independent suspension |
| CN204749770U (en) * | 2015-06-03 | 2015-11-11 | 同济大学 | Combine electromagnetism of cam to present two xarms initiative suspensions of ability formula |
-
2016
- 2016-04-12 CN CN201610222852.4A patent/CN105818627B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2434129A (en) * | 2004-03-12 | 2007-07-18 | Honda Motor Co Ltd | Suspension device |
| EP2165862A1 (en) * | 2008-09-23 | 2010-03-24 | Audi AG | Device for adjusting a wheel of a wheel suspension |
| CN201685676U (en) * | 2010-01-18 | 2010-12-29 | 简式国际汽车设计（北京）有限公司 | Double transverse arm independent suspension frame |
| CN201914045U (en) * | 2010-12-15 | 2011-08-03 | 陈言平 | Shock-absorber assembly of double-wishbone independent suspension |
| CN203511207U (en) * | 2013-08-15 | 2014-04-02 | 上海通用汽车有限公司 | Double wishbone suspension and vehicle body equipment with double wishbone suspension |
| CN204249767U (en) * | 2014-10-27 | 2015-04-08 | 北奔重型汽车集团有限公司 | A kind of double cross arm independent suspension |
| CN204749770U (en) * | 2015-06-03 | 2015-11-11 | 同济大学 | Combine electromagnetism of cam to present two xarms initiative suspensions of ability formula |
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