CN104097477B - Leading arm and lower leading arm length calculation method on a kind of double cross arm independent suspension - Google Patents
Leading arm and lower leading arm length calculation method on a kind of double cross arm independent suspension Download PDFInfo
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Abstract
The present invention relates to leading arm and lower leading arm length calculation method on a kind of double cross arm independent suspension.Purpose is in that to provide a kind of method calculating the upper and lower leading arm brachium of double cross arm independent suspension fast, accurately；Utilizing the constraintss such as Geometric Modeling emulation wheel alignment parameter change and suspension frame structure Geometrical change amount, building analytical geometry model, thus quickly, accurately determining leading arm length.It is mainly technically characterized ny the method utilizing CAD Geometric Modeling and analytical geometry, emulation double cross arm independent suspension is by when being fully loaded with Light Condition, the change of jumping and caused Wheel centre distance and camber angle on vehicle body, constant by leading arm brachium again, vehicle body waits other geometry constraint conditions together with the vertically upper jumping of spherical hinge central point, geometrical relationship according to its leading arm right angled triangle, even vertical structure analytical model, to calculate leading arm brachium.The present invention have Top-Down Design, accurately, the succinct feature such as directly perceived, provide a kind of reference for the original exploitation of suspension, improve efficiency of research and development.
Description
Invention field
The present invention relates to automotive suspension leading arm computational methods, especially relate to leading arm and lower leading arm length calculation method on a kind of double cross arm independent suspension.
Background technology
Double cross arm independent suspension is the suspension frame structure that Hyundai Motor is conventional.Its tectonic relationship is as shown in Figure 1: vehicle body is connected with upper leading arm 4 by upper leading arm inner hinge 6, is connected with lower leading arm 11 by lower leading arm inner hinge 13 meanwhile.Upper leading arm 4 is connected with knuckle 2 by the outer spherical hinge 3 of upper leading arm, and lower leading arm 11 is connected with knuckle by the outer spherical hinge 14 of lower leading arm.Knuckle 2 is connected by parts such as bearing, wheel hub, bolt and wheel rims with wheel 1, and knuckle 2 can not relative motion with wheel 1 and above-mentioned connector.When vehicle body because when load change moves up and down, its movement relation is: upper leading arm inner hinge 4 promotes the outer spherical hinge 2 of upper leading arm 3, upper leading arm to do plane motion in YOZ plane；Same lower leading arm inner hinge 5 promotes lower leading arm 6, the outer spherical hinge 7 of lower leading arm to do plane motion in YOZ plane；The outer spherical hinge 2 of upper leading arm and the outer spherical hinge 7 of lower leading arm drive knuckle 8 and wheel 1 to do plane motion in YOZ plane.
According to automotive suspension design theory, by the known double cross arm independent suspension leading arm length of above-mentioned movement relation to wheel alignment parameter important, therefore how to choose rational leading arm brachium and ensure that the positional parameter allowed change is particularly important.At present, determine double cross arm independent suspension leading arm brachium method, often rule of thumb or general layout requirement, first assume a brachium, then following methods analysis and solution it is generally adopted: (1) adopts many-body dynamics software ADAMS to set up three-dimensional simulation model, model is carried out dynamic analysis and optimization, to determine its rational hard spot coordinate；(2) utilize the analytic method such as coordinate transform and instantaneous center method, set up contacting of suspension space geometry and kinematics characteristic, so that it is determined that leading arm length；(3) empirical method, is also called examination and follows the example of.It is chosen over leading arm length according to the empirical equation that design data provides, checks camber angle change and wheelspan change, until satisfied.
Above method belongs to Reverse Design.It is primarily present following weak point: method (1) requires ADAMS professional software support, operator's professional standards and computer software application Capability Requirement are high.Method (2) system constructing is complicated, and efficiency is low, poor intuition.Method (3) needs repeatedly to calculate examination and takes, and computational accuracy cannot be guaranteed.Therefore, needing offer one badly and calculate simple, efficiency is high, the method for designing of highly versatile.
Summary of the invention
It is an object of the invention to provide a kind of method calculating the upper and lower leading arm brachium of double cross arm independent suspension fast, accurately；This invention utilizes kinematic constraint that Geometric Modeling emulation wheel alignment parameter change, suspension frame structure Geometrical change amount, sprung parts relative position and leading arm inner hinge central point can not move in Y direction and the constant constraints of brachium, build analytical geometry model and analytical model, thus quickly, accurately determining leading arm length.
The technical scheme is that and provide leading arm and lower leading arm length calculation method on a kind of double cross arm independent suspension, it is characterised in that:
Step 1, sets up YOZ coordinate system, Y coordinate axle is camber angle wheel axis when being 0 °, is just outwards；Z coordinate axle is cross the plumb line in wheel axis lengthwise position on vehicle body central fore-and-aft vertical plane, is just upwards；In the coordinate system, building fully loaded and the simplification of Light Condition double cross arm independent suspension plane geometry model respectively, it is accomplished by:
Step 1.1, double cross arm independent suspension is carried out geometry simplification；
Under step 1.2, full load condition, it is determined that upper leading arm ectosphere hinge centres point C, the position of lower leading arm ectosphere hinge centres point B；
Under step 1.3, full load condition, it is determined that the above Z-direction position of leading arm inner hinge central point D, lower leading arm inner hinge central point A, and assume their Y-direction position；
Step 1.4, utilize the upper leading arm ectosphere hinge centres point C that determines and lower leading arm ectosphere hinge centres point B and the position of the upper leading arm inner hinge central point D assumed and lower leading arm inner hinge central point A, set up full load condition suspension geometry model；
Step 1.5, from being fully loaded with to Light Condition, it is determined that upper leading arm ectosphere hinge centres point C ', the position of lower leading arm ectosphere hinge centres point B '；
Step 1.6, from being fully loaded with to Light Condition, it is determined that upper leading arm inner hinge central point C ', the Z-direction change location of lower leading arm inner hinge 13 central point B '；
Step 1.7, utilize determine the upper leading arm ectosphere hinge centres point C ' of Light Condition, lower leading arm ectosphere hinge centres point B ', upper leading arm inner hinge central point D ', lower leading arm inner hinge central point A ' position, set up Light Condition suspension geometry model；
Step 2, by under the fully loaded and Light Condition determined, the geometrical relationship of upper leading arm and lower leading arm, set up analytical geometry model, calculate and obtain upper leading arm and lower leading arm brachium；It is accomplished by:
Step 2.1, set up under full load condition, lower leading arm length analytical model；
y1 2+h1 2=l1 2(1)
Wherein: y1For the Y-direction relative distance of leading arm inner hinge central point A under full load condition and ectosphere hinge centres point B, h1Poor for lower leading arm inner hinge central point A and ectosphere hinge centres point B height, l1For lower leading arm length；
Step 2.2, set up zero load leading arm length analytical model at present；
(y1-Δy1)2+(h1+h-Δz1)2=l1 2(2)
Wherein: y1For the Y-direction relative distance of leading arm inner hinge central point A under full load condition and ectosphere hinge centres point B, h1Poor for lower leading arm inner hinge central point A and ectosphere hinge centres point B height, l1For lower leading arm length；Δy1Y-direction for being fully loaded with Light Condition leading arm ectosphere hinge centres point B to B ' at present changes distance, Δ z1Z-direction for being fully loaded with Light Condition leading arm ectosphere hinge centres point B to B ' at present changes distance, and h is the Z-direction change distance being fully loaded with Light Condition leading arm inner hinge central point A to A ' at present；
Due to Δ y1(mm)、Δz1(mm) by geometric model measures acquisition, h1, h be known quantity, calculate two known variables l by equation (1) and (2)2、y2Value, thus obtaining lower leading arm length；
Step 2.3, set up leading arm length analytical model on full load；
y2 2+h2 2=l2 2(3)
Wherein: y2For the Y-direction relative distance of leading arm inner hinge central point D and ectosphere hinge centres point C upper under full load condition, h2For upper leading arm inner hinge central point D and ectosphere hinge centres point C difference in height, l2For upper leading arm brachium；
Step 2.4, foundation upper leading arm length analytical model time unloaded；
(y2+Δy2)2+(h2-h+Δz2)2=l2 2(4)
Wherein: y2For the Y-direction relative distance of leading arm inner hinge central point D and ectosphere hinge centres point C upper under full load condition, h2For upper leading arm inner hinge central point D and ectosphere hinge centres point C difference in height, l2Upper leading arm brachium, Δ y2During for being fully loaded with Light Condition, the Y-direction of upper leading arm ectosphere hinge centres point C to C ' changes distance, Δ z2During for being fully loaded with Light Condition, the Z-direction of upper leading arm ectosphere hinge centres point C to C ' changes distance, the Z-direction change distance of upper leading arm inner hinge central point D to D ' when h is be fully loaded with Light Condition；
Due to Δ y2(mm)、Δz2(mm) by geometric model measures acquisition, h2, h be known quantity, calculate two known variables l by equation (3) and (4)2、y2Value, thus obtaining upper leading arm length.
The invention has the beneficial effects as follows:
1) the method geometric model adopts two dimensional surface modeling, and model construction is simple, makes designer not grasp professional software, or does not possess space mechanism's foundation of geometry of complexity, only possesses CAD basis, just can quickly, accurately realize operation.
2) the method analytical model is simple and practical, accurately reliably.Solve and utilize space mechanism to learn the complexity in modeling, tediously long mathematical derivation, the problem that converts and utilize simulation software repeatedly to optimize, improve design efficiency.
3) the method adopts forward method for designing, provides a kind of reference method for automotive suspension Original Architectural Design.
Accompanying drawing illustrates:
Fig. 1 is the double cross arm independent suspension structure used by this method；
Fig. 2 is double cross arm independent suspension Simplified two-dimension structure；
Fig. 3 is the fully loaded geometric model schematic diagram of double cross arm independent suspension；
Fig. 4 is the fully loaded and unloaded geometric model schematic diagram of double cross arm independent suspension；
Fig. 5 is leading arm geometrical relationship schematic diagram under fully loaded and zero load；
Fig. 6 is leading arm geometrical relationship schematic diagram in fully loaded and zero load.
Wherein: 1-wheel, 2-knuckle, the outer spherical hinge of the upper leading arm of 3-, the upper leading arm of 4-, 5-amortisseur, 6-shock absorber support, the upper leading arm inner hinge of 7-, the upper leading arm support of 8-, 9-torsion-bar spring, 10-limited block, leading arm under 11-, leading arm support under 12-, leading arm inner hinge under 13-, the outer spherical hinge of leading arm under 14-.
Detailed description of the invention
Below with reference to accompanying drawing 1-6, the specific embodiment of the present invention is described in detail.
As it is shown in figure 1, double cross arm independent suspension leading arm system of the present invention, including knuckle 2, the outer spherical hinge 3 of upper leading arm, upper leading arm 4, amortisseur 5, shock absorber support 6, upper leading arm inner hinge 7, upper leading arm support 8, torsion-bar spring 9, limited block 10, the outer spherical hinge 14 of lower leading arm 11, lower leading arm support 12, lower leading arm inner hinge 13 and lower leading arm；Wherein, upper leading arm support 8, lower leading arm support 12 are secured by bolts in vehicle body.Vehicle body is connected with upper leading arm 4 by upper leading arm inner hinge 7, is connected with lower leading arm 11 by lower leading arm inner hinge 13 meanwhile.Upper leading arm 4 is connected with knuckle 2 by the outer spherical hinge 3 of upper leading arm, and lower leading arm 11 is connected with knuckle by the outer spherical hinge 14 of lower leading arm.Knuckle 2 is connected by parts such as bearing, wheel hub, bolt and wheel rims with wheel 1, and knuckle 2 can not relative motion with wheel 1 and above-mentioned connector.Amortisseur 5 is connected with lower leading arm 11 by shock absorber support 6, is connected with vehicle body by shock absorber support 6.Vehicle body is fixed in torsion-bar spring 9 rear end, and front end is connected with lower leading arm 11 by joint, and limited block 10 is secured by bolts in lower leading arm.
Vehicle body because of load change up and down time, leading arm length can pass through hinge centres point shift in position affect the change of camber angle and wheelspan；Contrary, camber angle and wheelspan variable quantity and vehicle body jerk value also can pass through hinge centres point shift in position affects leading arm brachium.This mutual relation is utilized reversely to push over leading arm length.Therefore, if setting initial hinge centres point position, when the load is varied, control camber angle and wheelspan change and vehicle body jerk value in regulation allowed band, just corresponding hinge centres point shift in position amount can be obtained, thus being met the camber angle of control and the leading arm brachium of wheelspan change and vehicle body jerk value.
In the present embodiment, choose fully loaded and unloaded two typical condition states, it is noted that vehicle body is because symmetry constraint can only vertical be beated, and leading arm inner hinge central point can not move in Y-direction, and meanwhile, leading arm length is constant.
Utilize the two constraints, and inner hinge central point retrains with the constraint of outer ball pivot central point relative altitude, the relative wheel rim inner headed face relative position constraint of outer ball pivot central point, camber angle and wheelspan variable quantity, sets up the geometric model under two states.
Utilize the right angle trigonometry geometrical relationship that leading arm and projection thereof are constituted and the relation of hinge centres point shift in position amount, just can set up analytical model；Owing to leading arm brachium is constant, the analytical model set up based on right angle trigonometry geometrical relationship under simultaneous two states, leading arm length can be solved.
Generally when studying motion and the geometrical relationship of suspension, when not affecting computational accuracy, it is necessary to suspension frame structure is simplified.Therefore, in this embodiment, owing to automotive suspension is lateral symmetry, it is possible to select 1/2nd modelings that suspension is horizontal.Simultaneously as under both states, vehicle body and wheel do not vertically move, therefore can at transverse plane modeling analysis.In practical work process, Suspension movement form is unrelated with parts shape, only relevant with hinge centres point line, therefore, in this embodiment, deletes amortisseur, spring, limited block to Modeling Calculation independent component.Fig. 1 is simplified, result after simplification is as shown in Figure 2, the solid straight line that upper leading arm inner hinge 7 central point is connected with outer spherical hinge 3 central point of upper leading arm represents upper leading arm 4, the solid straight line that lower leading arm inner hinge 13 central point is connected with outer spherical hinge 14 central point of lower leading arm represents lower leading arm 11, and the solid straight line that outer spherical hinge 3 central point of upper leading arm is connected with outer spherical hinge 14 central point of lower leading arm represents knuckle 2.
In geometric model after simplification, relevant parameter definition is as follows: α is camber angle, and unit is °；β is kingpin inclination, and unit is °；B is kingpin offset, and unit is mm；D is tire radius, and unit is mm；S is tyre width, and unit is mm；Φ rim diameter, unit is mm.
Based on above analysis, the present invention proposes leading arm and lower leading arm length calculation method on a kind of double cross arm independent suspension, and step is as follows:
Step 1, sets up YOZ coordinate system, Y coordinate axle is camber angle wheel axis when being 0 °, is just outwards；Z coordinate axle is cross the plumb line in wheel axis lengthwise position on vehicle body central fore-and-aft vertical plane, is just upwards；In the coordinate system, respectively fully loaded with under Light Condition, structure is fully loaded with the plane geometry model simplified with Light Condition suspension.
This step utilizes diameter of tyres, rim diameter, hinge centres point, and from inside and outside wheel rim distance, incipient wheel camber angle, kingpin inclination, kingpin offset and hinge, the constraints of central point difference in height is to determine full load hinge centres point, thus setting up full load condition plane geometry model.
On the basis of fully loaded geometric model, hinge centres point when utilizing vehicle body vertical jitter amount and the relevant camber angle of designing requirement and the constraints of wheelspan variable quantity to determine zero load, set up Light Condition plane geometry model, wherein:
Step 1.1, suspension frame structure is carried out geometry simplification.
As it is shown on figure 3, wheel 1 can be simplified to wheel center line, wheel hub and the connector such as bearing, bolt thereof to be simplified to hub axis, knuckle 2 is simplified to main pin axis, and leading arm is simplified to hinge centres point line, and hinge is simplified to hinge centres point.
Step 1.2, determine the outer spherical hinge 3 central point C of upper leading arm, the position of the outer spherical hinge 14 central point B of lower leading arm.
By incipient wheel camber angle α (°), diameter of tyres and rim diameter, set up and simplify wheel model and vertical reference line, wheel center line when being 0 ° that vertical reference line is camber angle, characterize camber angle；Tire size is referred to tyre model.
During initial full load condition, the theoretical and designing requirement according to Automobile Design, in order to avoid outer ball pivot is interfered with wheel rim, outer ball pivot central point certain distance reserved with wheel rim periphery during design；In order to obtain aligning torque during steering reversal, preset certain kingpin inclination and kingpin offset.
With reference to wheel model reference line, by the outer ball pivot center of kingpin inclination β (°), kingpin offset b (mm) and leading arm and wheel rim periphery distance h3(mm), h4(mm), it is determined that the outer spherical hinge 3 central point C of upper leading arm, the position of the outer spherical hinge 14 central point B of lower leading arm.
Step 1.3, determine the Z-direction position of upper leading arm inner hinge 7 central point D, lower leading arm inner hinge 13 central point A, and assume their Y-direction position.
Theoretical and the designing requirement according to Automobile Design, in order to prevent suspension from transshipping at present, leading arm 11 bottom amplitude is excessive, designs leading arm inner hinge 13 central point A at present and is generally greater than outer ball pivot 14 central point B；Simultaneously taking account of height of roll center unsuitable too high, upper leading arm inner hinge 7 central point D is generally below outer ball pivot 3 central point C, utilizes lower leading arm inner hinge 13 central point A and outer spherical hinge 14 central point B height difference h1, and upper leading arm inner hinge 7 central point D and outer spherical hinge 3 central point C difference in height h (mm)2(mm), determine that lower leading arm inner hinge 13 central point B is hinged relative to ectosphere the Z-direction position of 14 central point B respectively, and upper leading arm inner hinge 7 central point D is hinged relative to ectosphere the Z-direction position of 3 central point C, here only can determine that the Z-direction position of leading arm inner hinge central point, it is impossible to determine Y-direction position.But in order to image shows to simplify the geometrical relationship of structure, Y-direction relative position is set to a variable.
Spherical hinge 3 central point C and the outer spherical hinge 14 central point B of lower leading arm outside the upper leading arm that step 1.4, utilization are determined, and the position of the upper leading arm inner hinge 7 central point D assumed and lower leading arm inner hinge 13 central point A, set up full load condition suspension geometry model.
As it is shown on figure 3, wherein: AB is lower leading arm plane geometry model, and BC is knuckle plane geometry model, and CD is upper leading arm plane geometry model.A is leading arm inner hinge central point under full load, and B is leading arm ectosphere hinge centres point under full load, and C is leading arm ectosphere hinge centres point on full load, and D is leading arm inner hinge 7 central point on full load.Wherein: α (°) is camber angle, β (°) is kingpin inclination, and b (mm) is kingpin offset.
h1(mm) for the Z-direction difference in height of lower leading arm 11 two ends hinge centres；h2(mm) for upper leading arm 4 two ends hinge centres Z-direction difference in height；h3(mm) for outer ball pivot 14 central point of lower leading arm and wheel rim periphery distance；h4(mm) for outer ball pivot 3 central point of upper leading arm and wheel rim periphery distance, for the vehicle determined, these parameters are all the design parameters determined in Car design process, therefore, in the calculating of this embodiment, for arbitrary design vehicle, this tittle is all known.
Now, owing to the Y-direction relative distance of upper leading arm inner hinge 7 central point D and outer spherical hinge 3 central point C, the lower leading arm inner hinge 13 central point A of upper leading arm and the outer spherical hinge 14 central point B of lower leading arm introduces variable, therefore, in geometric model, length shown by upper leading arm 4, lower leading arm 11 is the unknown quantity needing to solve.
Step 1.5, when by when being fully loaded with Light Condition, according to the Parameters variation that design vehicle is given, it is determined that upper leading arm outer spherical hinge 3 central point C ' time unloaded, the position of the outer spherical hinge 14 central point B ' of lower leading arm.
In this step, control camber angle, wheelspan and kingpin inclination change in regulation allowed band, according to different Car design requirements, general camber angle-2 °/50mm to 0.5 °/50mm of change (single-wheel bump amount), single-wheel wheelspan change-5mm/50mm to 5mm/50mm, kingpin inclination change with camber angle change, utilize the variable quantity scope that these are determined, as camber angle changes delta α (°), kingpin inclination changes delta β (°), wheelspan changes delta s1And the outer ball pivot center of leading arm and wheel rim periphery distance h (mm)3(mm), h4(mm), it may be determined that upper leading arm outer spherical hinge 3 central point C ' time unloaded, the position of the outer spherical hinge 14 central point B ' of lower leading arm.
Step 1.6, when by when being fully loaded with Light Condition, according to the Parameters variation that design vehicle is given, it is determined that upper leading arm inner hinge 7 central point D ', the Z-direction change location of lower leading arm inner hinge 13 central point A '.
Utilize the distance h (mm) of saltus step in vehicle body Z-direction, and change without Y-direction, it is determined that upper leading arm inner hinge 7 central point D ', the Z-direction change location of lower leading arm inner hinge 13 central point A '.Here vehicle body is vertically gone up jumping amount and should be met design requirement, and is maintained within a certain range, and is generally about 50mm.
Outside the outer spherical hinge 3 central point C ' of upper leading arm of the Light Condition that step 1.7, utilization are determined, lower leading arm, the position of spherical hinge 14 central point B ', upper leading arm inner hinge 7 central point D ', lower leading arm inner hinge 13 central point A ', sets up Light Condition suspension geometry model.
Such as Fig. 5, real contour line is the state of full load, dotted outline is state during zero load, wherein: A ' is zero load leading arm inner hinge center at present, B ' is zero load leading arm ectosphere hinge centres at present, C ' is upper leading arm ectosphere hinge centres when being unloaded, and D ' is upper leading arm inner hinge center when being unloaded.
H (mm) is jumping amount, Δ s on vehicle body when fully loaded and Light Condition1(mm) for being fully loaded with 1/2nd of Light Condition wheelspan change, Δ α (°) is for being fully loaded with the change of Light Condition camber angle, and Δ β (°) is for being fully loaded with the change of Light Condition kingpin inclination.
Step 2, by the geometrical relationship of leading arm and lower leading arm in the fully loaded and zero load determined in step 1, set up analytical geometry model, calculate and obtain upper leading arm and lower leading arm brachium.
As shown in Figure 5, Figure 6, unknown Y-direction position, inner hinge center, lower leading arm brachium l here1, upper leading arm brachium l2Not actual brachium, but in order to vivid shows its triangle relation, if a variable.
Step 2.1, set up leading arm length analytical model under full load；
y1 2+h1 2=l1 2(1)
Wherein: y1For the Y-direction relative distance of leading arm inner hinge 13 central point A and outer spherical hinge 14 central point B, h under full load condition1Poor for lower leading arm inner hinge 13 central point A and outer spherical hinge 14 central point B height, l1For lower leading arm brachium.
Step 2.2, set up zero load leading arm length analytical model at present；
(y1-Δy1)2+(h1+h-Δz1)2=l1 2(2)
Wherein: y1、h1、l1With (1), y1For the Y-direction relative distance of leading arm inner hinge 13 central point A and outer spherical hinge 14 central point B, h under full load condition1Poor for lower leading arm inner hinge 13 central point A and outer spherical hinge 14 central point B height, l1For lower leading arm brachium.Δy1For being fully loaded with the Y-direction change distance of outer spherical hinge 14 central point B to the B ' of Light Condition leading arm at present, Δ z1For being fully loaded with the Z-direction change distance of outer spherical hinge 14 central point B to the B ' of Light Condition leading arm at present, jumping amount on vehicle body when h is for being fully loaded with Light Condition, the Z-direction being namely fully loaded with Light Condition leading arm inner hinge 13 central point A to A ' at present changes distance.
It is lower leading arm 11 full load condition by Fig. 5 solid line AB part, lower leading arm brachium l1Respectively to Y-axis, Z axis projection, obtain Y-axis projected edge length y1, inside and outside hinge centres point height difference h1(mm) for Z axis projected edge length.Then, projected edge length y1(mm)、h1(mm) together with lower leading arm brachium l1Constitute a right angled triangle AOB, and meet Pythagorean theorem geometrical relationship, just can build one containing two known variables l1、y1Equation (1).
By step 1.5,1.6 determine be fully loaded with zero load lower leading arm 11 inside and outside spherical hinge center position variable quantity, namely under full load, leading arm inner hinge center A point is jumped h (mm) in Z-direction and is arrived zero load leading arm inner hinge center A ' at present, and under full load, leading arm ectosphere hinge centres B point is respectively along Y-axis, Z axis changes delta y1(mm)、Δz1(mm), zero load leading arm ectosphere hinge centres B ' at present is arrived.
In this embodiment, carry survey tool with graphics software and measure the outer spherical hinge 14 central point B of lower leading arm in Y, Z-direction projection change distance, measure Δ y1(mm)、Δz1(mm)；
By step 1.6, on vehicle body, jumping amount h (mm) is designing requirement amount, according to different vehicles, should maintain certain limit, be generally about 50mm, can be set to known constant.
If Fig. 5 dotted line A ' B ' part is lower leading arm 11 Light Condition, due to the constraint that leading arm brachium is constant, zero load is leading arm brachium l at present1(mm), based on hinge centres point change in location relation, more respectively to Y-axis, Z axis projection, projected edge length is changed to y respectively1-Δy1(mm)、h1+h-Δz1(mm), projected edge length is together with lower leading arm brachium l1(mm) constitute a right angled triangle A ' O ' B ', and meet Pythagorean theorem geometrical relationship, it is also possible to build one containing two known variables l1、y1Equation (2).
By step 1.3, lower leading arm 11 two ends hinge centres point height difference h1(mm) for Known designs required amount.Then, (1), (2) equation can go out lower leading arm brachium l by simultaneous solution1。
Step 2.3, set up leading arm length analytical model on full load；
y2 2+h2 2=l2 2(3)
Wherein: y2For the Y-direction relative distance of leading arm inner hinge 7 central point D and outer spherical hinge 3 central point C, h in full load condition2For upper leading arm inner hinge 7 central point D and outer spherical hinge 3 central point C difference in height, l2For upper leading arm brachium.
Step 2.4, foundation upper leading arm length analytical model time unloaded；
(y2+Δy2)2+(h2-h+Δz2)2=l2 2(4)
Wherein: y2、h2、l2With (3), y2For the Y-direction relative distance of leading arm inner hinge 7 central point D and outer spherical hinge 3 central point C, h in full load condition2For upper leading arm inner hinge 7 central point D and outer spherical hinge 3 central point C difference in height, l2For upper leading arm brachium.Δy2During for being fully loaded with Light Condition, the Y-direction of outer spherical hinge 3 central point C to the C ' of upper leading arm changes distance, Δ z2The Z-direction change distance of upper leading arm outer spherical hinge 3 central point C to C ' during for being fully loaded with Light Condition, jumping amount on vehicle body when h is for being fully loaded with Light Condition, when being namely fully loaded with Light Condition, above the Z-direction of leading arm inner hinge 7 central point D to D ' changes distance.
It is upper leading arm 4 full load condition by Fig. 6 solid line CD part, upper leading arm brachium l2Respectively to Y-axis, Z axis projection, obtain Y-axis projected edge length y2, inside and outside hinge centres point height difference h2(mm) for Z axis projected edge length.Then, projected edge length y2(mm)、h2(mm) together with upper leading arm brachium l2Constitute a right angled triangle CPD, and meet Pythagorean theorem geometrical relationship, just can build one containing two known variables l2、y2Equation (3).
By step 1.5,1.6 determine be fully loaded with zero load upper leading arm inside and outside spherical hinge center variable quantity, namely on full load, leading arm inner hinge center D point jumps upper leading arm inner hinge center D ' when h (mm) arrives unloaded in Z-direction, and on full load, leading arm ectosphere hinge centres C point is respectively along Y-axis, Z axis changes delta y1(mm)、Δz1(mm) upper leading arm ectosphere hinge centres C ' when, arriving unloaded.
In this embodiment, carry survey tool with graphics software and measure upper leading arm ectosphere hinge centres point 3 in Y, Z-direction projection change distance, measure Δ y2(mm)、Δz2(mm), on vehicle body, jumping amount h (mm) is known.
If Fig. 6 dotted line C ' D ' part is upper leading arm 4 Light Condition, due to the constraint that leading arm brachium is constant, upper leading arm brachium l time unloaded2(mm), based on the hinge centres point change in location relation of step 2.5, more respectively to Y-axis, Z axis projection, projected edge length is changed to y respectively2+Δy2(mm)、h2-h+Δz2(mm), projected edge length is together with upper leading arm brachium l2(mm) constitute a right angled triangle C ' P ' D ', and meet Pythagorean theorem geometrical relationship, it is also possible to build one containing two known variables l2、y2Equation (4).
By step 1.3, upper leading arm 4 two ends hinge centres point height difference h2(mm) for Known designs required amount.(3), (4) equation can go out upper leading arm brachium by simultaneous solution.
Below with reference to accompanying drawing, introducing an example calculation, its parameter value comes from certain electronic guide to visitors car.To be fully loaded with for original state, the just fixed wheel alignment parameter such as following table and structure arrangement parameter, emulate by when being fully loaded with Light Condition, control vehicle body is jumped, camber angle and wheelspan etc. change, and simplified structural modal is to geometric model.Here only in Geometric Modeling environment, survey tool need to be carried with software and measures spherical hinge central point inside and outside leading arm and, in Y, Z-direction projection change distance, measure Δ y2(mm) for-2.9806 (upper leading arm Y-direction projected length diminishes), Δ z2(mm) it is 1.156, Δ y1(mm) it is 7.0031, Δ z1(mm) it is 0.6264；Substitute into analytic equation (1), (2), (3) and (4), just can calculate leading arm brachium.Detail parameters and result are shown in table 1 below:
Table 1 suspension geometry parameter and brachium result table
Although disclose in detail the present invention with reference to accompanying drawing, it will be appreciated that, these describe merely exemplary, are not used for limiting the application of the present invention.Protection scope of the present invention is by appended claims, and various modification, remodeling and the equivalents made for invention when may be included in without departing from scope and spirit.
Claims (1)
1. leading arm and lower leading arm length calculation method on a double cross arm independent suspension, it is characterised in that:
Step 1, sets up YOZ coordinate system, Y coordinate axle is camber angle wheel axis when being 0 °, is just outwards；Z coordinate axle is cross the plumb line in wheel axis lengthwise position on vehicle body central fore-and-aft vertical plane, is just upwards；In the coordinate system, building fully loaded and the simplification of Light Condition double cross arm independent suspension plane geometry model respectively, it is accomplished by:
Step 1.1, double cross arm independent suspension is carried out geometry simplification；
Under step 1.2, full load condition, it is determined that outer spherical hinge (3) the central point C of upper leading arm, the position of outer spherical hinge (14) the central point B of lower leading arm；
Under step 1.3, full load condition, it is determined that the above Z-direction position of leading arm inner hinge (7) central point D, lower leading arm inner hinge (13) central point A, and assume their Y-direction position；
Spherical hinge (3) central point C and outer spherical hinge (14) the central point B of lower leading arm outside the upper leading arm that step 1.4, utilization are determined, and the position of upper leading arm inner hinge (7) the central point D assumed and lower leading arm inner hinge (13) central point A, set up full load condition suspension geometry model；
Step 1.5, from being fully loaded with to Light Condition, it is determined that outer spherical hinge (3) the central point C ' of upper leading arm, the position of outer spherical hinge (14) the central point B ' of lower leading arm；
Step 1.6, from being fully loaded with to Light Condition, it is determined that upper leading arm inner hinge (7) central point C ', the Z-direction change location of lower leading arm inner hinge 13 central point B '；
Outside outer spherical hinge (3) the central point C ' of upper leading arm of the Light Condition that step 1.7, utilization are determined, lower leading arm, the position of spherical hinge (14) central point B ', upper leading arm inner hinge (7) central point D ', lower leading arm inner hinge (13) central point A ', sets up Light Condition suspension geometry model；
Step 2, by under the fully loaded and Light Condition determined, the geometrical relationship of upper leading arm and lower leading arm, set up analytical geometry model, calculate and obtain upper leading arm and lower leading arm brachium；It is accomplished by:
Step 2.1, set up under full load condition, lower leading arm length analytical model；
Wherein: y1For the Y-direction relative distance of leading arm inner hinge (13) central point A and outer spherical hinge (14) central point B, h under full load condition1Poor for lower leading arm inner hinge (13) central point A and outer spherical hinge (14) central point B height, l1For lower leading arm length；
Step 2.2, set up zero load leading arm length analytical model at present；
Wherein: y1For the Y-direction relative distance of leading arm inner hinge (13) central point A and outer spherical hinge (14) central point B, h under full load condition1Poor for lower leading arm inner hinge (13) central point A and outer spherical hinge (14) central point B height, l1For lower leading arm length；Δy1For being fully loaded with the Y-direction change distance of outer spherical hinge (14) central point B to the B ' of Light Condition leading arm at present, Δ z1For being fully loaded with the Z-direction change distance of outer spherical hinge (14) central point B to the B ' of Light Condition leading arm at present, h is the Z-direction change distance being fully loaded with Light Condition leading arm inner hinge (13) central point A to A ' at present；
Due to Δ y1(mm)、Δz1(mm) by geometric model measures acquisition, h1, h be known quantity, calculate two known variables l by equation (1) and (2)2、y2Value, thus obtaining lower leading arm length；
Step 2.3, set up leading arm length analytical model on full load；
Wherein: y2For the Y-direction relative distance of leading arm inner hinge (7) central point D and outer spherical hinge (3) central point C upper under full load condition, h2For upper leading arm inner hinge (7) central point D and outer spherical hinge (3) central point C difference in height, l2For upper leading arm brachium；
Step 2.4, foundation upper leading arm length analytical model time unloaded；
Wherein: y2For the Y-direction relative distance of leading arm inner hinge (7) central point D and outer spherical hinge (3) central point C upper under full load condition, h2For upper leading arm inner hinge (7) central point D and outer spherical hinge (3) central point C difference in height, l2Upper leading arm brachium, Δ y2During for being fully loaded with Light Condition, the Y-direction of outer spherical hinge (3) central point C to the C ' of upper leading arm changes distance, Δ z2During for being fully loaded with Light Condition, the Z-direction of outer spherical hinge (3) central point C to the C ' of upper leading arm changes distance, the Z-direction change distance of upper leading arm inner hinge (7) central point D to D ' when h is be fully loaded with Light Condition；
Due to Δ y2(mm)、Δz2(mm) by geometric model measures acquisition, h2, h be known quantity, calculate two known variables l by equation (3) and (4)2、y2Value, thus obtaining upper leading arm length.
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| CN105082925B (en) * | 2015-09-18 | 2017-06-06 | 北汽福田汽车股份有限公司 | Stabilizer bar connecting bar and its manufacture method and vehicle |
| CN106529058B (en) * | 2016-11-17 | 2019-08-09 | 北京汽车研究总院有限公司 | A kind of method and apparatus of suspension forward sight geometry motion analysis |
| CN107985403B (en) * | 2017-11-09 | 2019-10-22 | 北汽福田汽车股份有限公司 | The design method of double cross arm independent suspension track rod cut-off point |
| CN110298129B (en) * | 2019-07-04 | 2022-09-23 | 河海大学常州校区 | Modeling method for telescopic vibration characteristic of straight-arm type aerial work platform arm support |
| CN110321664B (en) * | 2019-07-24 | 2022-07-26 | 厦门理工学院 | Macpherson suspension wheel track change determination method and device |
| CN113868764A (en) * | 2021-09-28 | 2021-12-31 | 南京依维柯汽车有限公司 | Nonlinear torsion bar spring independent suspension dynamics modeling and simulation method |
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| CN200988406Y (en) * | 2006-12-29 | 2007-12-12 | 比亚迪股份有限公司 | Multiple link rod suspension frame device |
| CN201501263U (en) * | 2009-09-24 | 2010-06-09 | 张海峰 | Combined bearing air suspension with air bags on identical side of axle |
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