CN104097477A - Length calculation method for upper guide arm and lower guide arm of double-cross-arm independent suspension - Google Patents
Length calculation method for upper guide arm and lower guide arm of double-cross-arm independent suspension Download PDFInfo
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- CN104097477A CN104097477A CN201410245758.1A CN201410245758A CN104097477A CN 104097477 A CN104097477 A CN 104097477A CN 201410245758 A CN201410245758 A CN 201410245758A CN 104097477 A CN104097477 A CN 104097477A
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Abstract
The invention relates to a length calculation method for an upper guide arm and a lower guide arm of a double-cross-arm independent suspension, and aims at providing a method for fast and precisely calculating the length of the upper guide arm and the length of the lower guide arm of the double-cross-arm independent suspension. An analytic geometric model is constructed by utilizing constraint conditions such as geometric modeling simulation wheel positioning parameter change and suspension structure geometric variation, so that the length of each guide arm is determined fast and precisely. The method is mainly technically characterized in that vehicle body jump and resultant changes on the wheel span and the wheel camber angle from a full load state to a no-load state of the double-cross-arm independent suspension are simulated by using methods of CAD (Computer-Aided Design) geometric modeling and analytic geometry; next, based on the unchanged length of each guide arm, vertical jump of a vehicle body together with the center point of a spherical hinge and other geometric constraint conditions, according to the geometric relationship of a right triangle of each guide arm, an analytic model is constructed to figure out the length of each guide arm. The method has the characteristics of forward design, precision, simplicity, intuitiveness and the like; a reference is provided for the original development of the suspension to improve the research and development efficiency.
Description
Invention field
The present invention relates to automotive suspension guide arm method of calculating, especially relate to guide arm and lower guide 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 modern automobile is conventional.Its tectonic relationship is as shown in Figure 1: vehicle body is connected with upper guide arm 4 by upper guide arm inner hinge 6,, by lower guide arm inner hinge 13, is connected with lower guide arm 11 meanwhile.Upper guide arm 4 is connected with steering swivel 2 by the outer spherical hinge 3 of upper guide arm, and lower guide arm 11 is connected with steering swivel by the outer spherical hinge 14 of lower guide arm.Steering swivel 2 is connected by parts such as bearing, wheel hub, bolt and wheel rims with wheel 1, and steering swivel 2 can not relative motion with wheel 1 and above-mentioned attaching parts.When vehicle body, because during load change up-and-down movement, its movement relation is: upper guide arm inner hinge 4 promotes upper guide arm 3, the outer spherical hinge 2 of upper guide arm is made plane motion in YOZ plane; Same lower guide arm inner hinge 5 promotes lower guide arm 6, the outer spherical hinge 7 of lower guide arm is made plane motion in YOZ plane; The outer spherical hinge 7 of the outer spherical hinge 2 of upper guide arm and lower guide arm drives steering swivel 8 and wheel 1 to make plane motion in YOZ plane.
According to automotive suspension design theory, by the known double cross arm independent suspension guide arm of above-mentioned movement relation length, to wheel alignment parameter important, therefore how to choose rational guide arm brachium and guarantee that the positional parameter variation allowing seems particularly important.At present, determine double cross arm independent suspension guide arm brachium method, often rule of thumb or general layout requirement, first suppose a brachium, then generally adopt following methods analysis and solution: (1) adopts many-body dynamics software ADAMS to set up three-dimensional simulation model, model is carried out to dynamics analysis and optimization, to determine its rational hard spot coordinate; (2) utilize the analysis method such as coordinate transform and instantaneous center method, set up contacting of suspension space geometry and kinematics characteristic, thereby determine guide arm length; (3) empirical method, is called again examination and follows the example of.The empirical equation providing according to design information is selective guide arm lengths repeatedly, checks camber angle variation and wheelspan and changes, until satisfied.
Above method belongs to Reverse Design.Mainly have the following disadvantages: method (1) requires the support of ADAMS professional software, high to operator's professional standards and computer software application Capability Requirement.Method (2) system constructing is complicated, and efficiency is low, and intuitive is poor.Method (3) need to repeatedly be calculated examination and get, and design accuracy cannot be guaranteed.Therefore, need badly and provide a kind of calculating simple, efficiency is high, the method for designing of highly versatile.
Summary of the invention
The object of the present invention is to provide a kind of method that calculates fast, accurately the upper and lower guide arm brachium of double cross arm independent suspension; Kinematic constraint and the constant constraint condition of brachium of in this invention, utilizing the variation of Geometric Modeling emulation wheel alignment parameter, suspension frame structure Geometrical change amount, sprung parts relative position and guide arm inner hinge center-point not to move in Y direction, build analytic geometry model and analytic model, thereby fast, accurately determine guide arm length.
Technical scheme of the present invention has been to provide guide arm and lower guide arm length calculation method on a kind of double cross arm independent suspension, it is characterized in that:
Step 1, sets up YOZ system of axes, and Y coordinate axle is camber angle wheel axis while being 0 °, outwards for just; Z coordinate axle is the plumb bob vertical of crossing on vehicle body center buttock in wheel axis lengthwise position, upwards for just; In this system of axes, build respectively plane geometry model fully loaded and that light condition double cross arm independent suspension is simplified, it is realized in the following manner:
Step 1.1, double cross arm independent suspension is carried out to geometry simplify;
Under step 1.2, fully laden, determine the outer spherical hinge center-point C of upper guide arm, the position of the outer spherical hinge center-point B of lower guide arm;
Under step 1.3, fully laden, determine the Z-direction position of upper guide arm inner hinge center-point D, lower guide arm inner hinge center-point A, and suppose their Y-direction position;
The outer spherical hinge center-point C of upper guide arm that step 1.4, utilization are determined and the outer spherical hinge center-point B of lower guide arm, and the upper guide arm inner hinge center-point D of hypothesis and the position of lower guide arm inner hinge center-point A, set up fully laden suspension geometry model;
Step 1.5, from being fully loaded with to light condition, determine the outer spherical hinge center-point C ' of upper guide arm, the position of the outer spherical hinge center-point B ' of lower guide arm;
Step 1.6, from being fully loaded with to light condition, determine upper guide arm inner hinge center-point C ', the Z-direction change location of lower guide arm inner hinge 13 center-point B ';
Step 1.7, utilize the position of the outer spherical hinge center-point C ' of upper guide arm of definite light condition, the outer spherical hinge center-point B ' of lower guide arm, upper guide arm inner hinge center-point D ', lower guide arm inner hinge center-point A ', set up light condition suspension geometry model;
Step 2, by under the fully loaded and light condition of determining, the geometric relationship of upper guide arm and lower guide arm, sets up analytic geometry model, calculates guide arm and lower guide arm brachium; It is realized in the following manner:
Step 2.1, set up under fully laden lower guide arm length analytic model;
y
1 2+h
1 2＝l
1 2 (1)
Wherein: y
1for the Y-direction relative distance of guide arm inner hinge center-point A under fully laden and outer spherical hinge center-point B, h
1for lower guide arm inner hinge center-point A and outer spherical hinge center-point B diff-H, l
1for lower guide arm length;
Step 2.2, set up zero load guide arm length analytic model at present;
(y
1-Δy
1)
2+(h
1+h-Δz
1)
2＝l
1 2 (2)
Wherein: y
1for the Y-direction relative distance of guide arm inner hinge center-point A under fully laden and outer spherical hinge center-point B, h
1for lower guide arm inner hinge center-point A and outer spherical hinge center-point B diff-H, l
1for lower guide arm length; Δ y
1for be fully loaded with light condition at present the outer spherical hinge center-point B of guide arm to the Y-direction variation distance of B ', Δ z
1for be fully loaded with light condition at present the outer spherical hinge center-point B of guide arm to the Z-direction of B ', change distance, h for be fully loaded with light condition at present guide arm inner hinge center-point A to the Z-direction variation distance of A ';
Due to Δ y
1(mm), Δ z
1(mm) by measuring acquisition, h in geometric model
1, h is known quantity, by equation (1) and (2), calculates two known variables l
2, y
2value, thereby obtain lower guide arm length;
Step 2.3, set up guide arm length analytic model at full load;
y
2 2+h
2 2＝l
2 2 (3)
Wherein: y
2for the Y-direction relative distance of upper guide arm inner hinge center-point D and outer spherical hinge center-point C under fully laden, h
2for upper guide arm inner hinge center-point D and outer spherical hinge center-point C diff-H, l
2for upper guide arm brachium;
Upper guide arm length analytic model when step 2.4, foundation zero load;
(y
2+Δy
2)
2+(h
2-h+Δz
2)
2＝l
2 2 (4)
Wherein: y
2for the Y-direction relative distance of upper guide arm inner hinge center-point D and outer spherical hinge center-point C under fully laden, h
2for upper guide arm inner hinge center-point D and outer spherical hinge center-point C diff-H, l
2upper guide arm brachium, Δ y
2the outer spherical hinge center-point C of upper guide arm is to the Y-direction variation distance of C ', Δ z when being fully loaded with light condition
2the outer spherical hinge center-point C of upper guide arm changes distance to the Z-direction of C ' when being fully loaded with light condition, h when being fully loaded with light condition upper guide arm inner hinge center-point D to the Z-direction variation distance of D ';
Due to Δ y
2(mm), Δ z
2(mm) by measuring acquisition, h in geometric model
2, h is known quantity, by equation (3) and (4), calculates two known variables l
2, y
2value, thereby obtain guide 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 complicated space mechanism's foundation of geometry, only possesses CAD basis, just can fast, accurately realize operation.
2) the method analytic model is simple and practical, accurately reliable.Solved and utilized space mechanism to learn the complexity in modeling, tediously long mathematical derivation, the problem that converts and utilize simulation software repeatedly to optimize, improved design efficiency.
3) the method adopts forward method of designing, for automotive suspension Original Architectural Design provides a kind of reference method.
Accompanying drawing explanation:
Fig. 1 is this method double cross arm independent suspension structure used;
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 that double cross arm independent suspension is fully loaded with and unloaded geometric model schematic diagram;
Fig. 5 is fully loaded and unloaded lower guide arm geometric relationship schematic diagram;
Fig. 6 is fully loaded and unloaded upper guide arm geometric relationship schematic diagram.
Wherein: 1-wheel, 2-steering swivel, the outer spherical hinge of the upper guide arm of 3-, the upper guide arm of 4-, 5-bumper, 6-shock absorber support, the upper guide arm inner hinge of 7-, the upper guide arm support of 8-, 9-torsion bar spring, 10-limiting stopper, guide arm under 11-, guide arm support under 12-, guide arm inner hinge under 13-, the outer spherical hinge of guide arm under 14-.
The specific embodiment
Below with reference to accompanying drawing 1-6, the specific embodiment of the present invention is elaborated.
As shown in Figure 1, double cross arm independent suspension guide arm system of the present invention, comprises steering swivel 2, the outer spherical hinge 3 of upper guide arm, upper guide arm 4, bumper 5, shock absorber support 6, upper guide arm inner hinge 7, upper guide arm support 8, torsion bar spring 9, limiting stopper 10, lower guide arm 11, lower guide arm support 12, the outer spherical hinge 14 of lower guide arm inner hinge 13 and lower guide arm; Wherein, upper guide arm support 8, lower guide arm support 12 are secured by bolts in vehicle body.Vehicle body is connected with upper guide arm 4 by upper guide arm inner hinge 7,, by lower guide arm inner hinge 13, is connected with lower guide arm 11 meanwhile.Upper guide arm 4 is connected with steering swivel 2 by the outer spherical hinge 3 of upper guide arm, and lower guide arm 11 is connected with steering swivel by the outer spherical hinge 14 of lower guide arm.Steering swivel 2 is connected by parts such as bearing, wheel hub, bolt and wheel rims with wheel 1, and steering swivel 2 can not relative motion with wheel 1 and above-mentioned attaching parts.Bumper 5 is connected with lower guide arm 11 by shock absorber support 6, by shock absorber support 6, is connected with vehicle body.Vehicle body is fixed in torsion bar spring 9 rear ends, and front end is connected with lower guide arm 11 by joint, and limiting stopper 10 is secured by bolts in lower guide arm.
When vehicle body changes up and down because of load, guide arm length can be by the variation of hinge center position influence of change camber angle and wheelspan; Contrary, camber angle and wheelspan variable quantity and vehicle body jerk value also can pass through hinge center position influence of change guide arm brachium.Utilize this interrelation oppositely to push over guide arm length.Therefore, if set initial hinge center position, when load change, control camber angle and wheelspan variation and vehicle body jerk value in regulation allowed band, just corresponding hinge center position variation be can obtain, thereby the camber angle of control and the guide arm brachium of wheelspan variation and vehicle body jerk value are met.
In the present embodiment, choose fully loaded and unloaded two typical condition states, notice vehicle body because symmetry constraint can only vertically be beated, guide arm inner hinge center-point can not move in Y-direction, and meanwhile, guide arm length is constant.
Utilize this two constraint conditions, and inner hinge center-point and the constraint of outer ball pivot center-point relative height, the relative wheel rim inner headed face of outer ball pivot center-point relative position constraint, camber angle and the constraint of wheelspan variable quantity, set up the geometric model under two states.
The right angle trigonometry geometric relationship of utilizing guide arm and projection thereof to form, and the relation of hinge center position variation, just can set up analytic model; Because guide arm brachium is constant, the analytic model of setting up based on right angle trigonometry geometric relationship under simultaneous two states, can solve guide arm length.
Conventionally when the research motion of suspension and geometric relationship, in the situation that not affecting design accuracy, need to simplify suspension frame structure.Therefore,, in this enforcement, due to automotive suspension lateral symmetry, can select 1/2nd horizontal modelings of suspension.Meanwhile, under this two states, vehicle body and wheel do not vertically move, therefore can be at Transverse plane modeling analysis.In practical work process, suspension mode of motion and parts shape are irrelevant, only relevant with hinge center-point line, therefore, in this embodiment, delete bumper, spring, limiting stopper to Modeling Calculation independent component.Fig. 1 is simplified, result after simplification as shown in Figure 2, the upper guide arm 4 of solid straight line representative that upper guide arm inner hinge 7 center-points are connected with outer spherical hinge 3 center-points of upper guide arm, the lower guide arm 11 of solid straight line representative that lower guide arm inner hinge 13 center-points are connected with outer spherical hinge 14 center-points of lower guide arm, outer spherical hinge 3 center-points of upper guide arm represent steering swivel 2 with the solid straight line that outer spherical hinge 14 center-points of lower guide arm are connected.
In geometric model after simplification, correlation parameter is defined as follows: α is camber angle, and unit is °; β is Kingpin inclination angle, and unit is °; B is swivelling radius, 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 guide arm and lower guide arm length calculation method on a kind of double cross arm independent suspension, step is as follows:
Step 1, sets up YOZ system of axes, and Y coordinate axle is camber angle wheel axis while being 0 °, outwards for just; Z coordinate axle is the plumb bob vertical of crossing on vehicle body center buttock in wheel axis lengthwise position, upwards for just; In this system of axes, under fully loaded and light condition, build plane geometry model fully loaded and that light condition suspension is simplified respectively.
This step utilizes diameter of tyres, rim diameter, hinge center-point to determine at full load hinge center-point apart from the constraint condition of center-point diff-H inside and outside wheel rim distance, initial camber angle, Kingpin inclination angle, swivelling radius and hinge, thereby sets up fully laden plane geometry model.
On the basis of fully loaded geometric model, while utilizing vehicle body vertical bounce amount and the relevant camber angle of designing requirement and the constraint condition of wheelspan variable quantity to determine zero load, hinge center-point, sets up light condition plane geometry model, wherein:
Step 1.1, suspension frame structure is carried out to geometry simplify.
As shown in Figure 3, wheel 1 can be simplified to wheel center line, the attaching partss such as wheel hub and bearing, bolt are simplified to hub axis, and steering swivel 2 is simplified to main pin axis, and guide arm is simplified to hinge center-point line, and hinge is simplified to hinge center-point.
Step 1.2, the outer spherical hinge 3 center-point C of definite upper guide arm, the position of the outer spherical hinge 14 center-point B of lower guide arm.
By initial camber angle α (°), diameter of tyres and rim diameter, set up and simplify wheel model and vertical line of reference, vertically line of reference is camber angle wheel center line while being 0 °, characterizes camber angle; Tire size can be with reference to tyre model.
During initial fully laden, according to automobile design theory and designing requirement, for fear of outer ball pivot and wheel rim, interfere the reserved certain distance of outer ball pivot center-point and wheel rim periphery during design; Aligning torque when obtaining steering reversal, default certain Kingpin inclination angle and swivelling radius.
With reference to wheel model reference line, by Kingpin inclination angle β (°), the outer ball pivot center of swivelling radius b (mm) and guide arm and wheel rim periphery distance h
3(mm), h
4(mm), determine the outer spherical hinge 3 center-point C of upper guide arm, the position of the outer spherical hinge 14 center-point B of lower guide arm.
Step 1.3, determine the Z-direction position of upper guide arm inner hinge 7 center-point D, lower guide arm inner hinge 13 center-point A, and suppose their Y-direction position.
According to automobile design theory and designing requirement, in order to prevent that suspension from transshipping that guide arm 11 bottom amplitudes are excessive at present, design at present guide arm inner hinge 13 center-point A generally higher than outer ball pivot 14 center-point B; Consider that height of roll center is unsuitable too high, upper guide arm inner hinge 7 center-point D, generally lower than outer ball pivot 3 center-point C, utilize lower guide arm inner hinge 13 center-point A and outer spherical hinge 14 center-point B diff-H h simultaneously
1, and upper guide arm inner hinge 7 center-point D and outer spherical hinge 3 center-point C diff-H h (mm)
2(mm), determine that respectively lower guide arm inner hinge 13 center-point B are with respect to the be hinged Z-direction position of 14 center-point B of ectosphere, and upper guide arm inner hinge 7 center-point D are with respect to the be hinged Z-direction position of 3 center-point C of ectosphere, here only can determine the Z-direction position of guide arm inner hinge center-point, can not determine Y-direction position.But for image shows the geometric relationship of simplified structure Y-direction relative position to be made as to a variable.
The outer spherical hinge 3 center-point C of upper guide arm that step 1.4, utilization are determined and the outer spherical hinge 14 center-point B of lower guide arm, and the upper guide arm inner hinge 7 center-point D of hypothesis and the position of lower guide arm inner hinge 13 center-point A, set up fully laden suspension geometry model.
As shown in Figure 3, wherein: AB is lower guide arm plane geometry model, and BC is steering swivel plane geometry model, CD is upper guide arm plane geometry model.A is guide arm inner hinge center-point under at full load, and B is the outer spherical hinge center-point of guide arm under at full load, and C is the outer spherical hinge center-point of guide arm at full load, and D is guide arm inner hinge 7 center-points at full load.Wherein: α (°) be camber angle, β (°) be Kingpin inclination angle, b (mm) is swivelling radius.
H
1(mm) be the Z-direction diff-H at lower guide arm 11 hinge centers, two ends; h
2(mm) be upper guide arm 4 hinge center, two ends Z-direction diff-Hs; h
3(mm) be outer ball pivot 14 center-points of lower guide arm and wheel rim periphery distance; h
4(mm) be outer ball pivot 3 center-points of upper guide arm and wheel rim periphery distance, for definite vehicle, these parameters are all design parameterss definite in vehicle design process, therefore, in the calculating of this embodiment, for arbitrary design vehicle, this tittle is all known.
Now, because the Y-direction relative distance of upper guide arm inner hinge 7 center-point D and outer spherical hinge 3 center-point C, the lower guide arm inner hinge 13 center-point A of upper guide arm and the outer spherical hinge 14 center-point B of lower guide arm is introduced variable, therefore, in geometric model, upper guide arm 4, the shown length of lower guide arm 11 are the unknown quantity that need to solve.
Step 1.5, when when being fully loaded with light condition, the parameter given according to design vehicle changes, and determines the outer spherical hinge 3 center-point C ' of upper guide arm when unloaded, the position of the outer spherical hinge 14 center-point B ' of lower guide arm.
In this step, controlling camber angle, wheelspan and Kingpin inclination angle changes in regulation allowed band, according to different vehicle designing requirements, general camber angle changes-2 °/50mm to 0.5 °/50mm (single-wheel bump amount), single-wheel wheelspan variation-5mm/50mm to 5mm/50mm, Kingpin inclination angle changes and to change with camber angle, utilize these definite variable quantity scopes, when camber angle changes delta α (°), Kingpin inclination angle changes delta β (°), wheelspan changes delta s
1and the outer ball pivot center of guide arm and wheel rim periphery distance h (mm)
3(mm), h
4(mm), the outer spherical hinge 3 center-point C ' of upper guide arm in the time of can determining zero load, the position of the outer spherical hinge 14 center-point B ' of lower guide arm.
Step 1.6, when when being fully loaded with light condition, the parameter given according to design vehicle changes, and determines upper guide arm inner hinge 7 center-point D ', the Z-direction change location of lower guide arm inner hinge 13 center-point A '.
Utilize the distance h (mm) of saltus step in vehicle body Z-direction, and change without Y-direction, determine upper guide arm inner hinge 7 center-point D ', the Z-direction change location of lower guide arm inner hinge 13 center-point A '.The vehicle body here is vertically gone up jumping amount and should be met design requirement, and is maintained within a certain range, and is generally 50mm left and right.
Step 1.7, utilize the position of the outer spherical hinge 3 center-point C ' of upper guide arm of definite light condition, the outer spherical hinge 14 center-point B ' of lower guide arm, upper guide arm inner hinge 7 center-point D ', lower guide arm inner hinge 13 center-point A ', set up light condition suspension geometry model.
As Fig. 5, the state that real outline line is at full load, state when dotted outline is unloaded, wherein: A ' is zero load guide arm inner hinge center at present, B ' is the zero load outer spherical hinge of guide arm center at present, the outer spherical hinge of upper guide arm center when C ' is unloaded, upper guide arm inner hinge center when D ' is unloaded.
H (mm) is jumping amount on vehicle body when fully loaded and light condition, Δ s
1(mm) for being fully loaded with 1/2nd of light condition wheelspan variation, Δ α (°) for being fully loaded with light condition camber angle, change, Δ β (°) for being fully loaded with light condition Kingpin inclination angle, change.
Step 2, by the geometric relationship of fully loaded and unloaded upper guide arm and the lower guide arm determined in step 1, set up analytic geometry model, calculate guide arm and lower guide arm brachium.
As shown in Figure 5, Figure 6, Y-direction position, unknown inner hinge center, the lower guide arm brachium l here
1, upper guide arm brachium l
2be not actual brachium, but for its triangle relation that shows of image, a variable of establishing.
Step 2.1, set up guide arm length analytic model under at full load;
y
1 2+h
1 2＝l
1 2 (1)
Wherein: y
1for the Y-direction relative distance of the 13 center-point A of guide arm inner hinge under fully laden and outer spherical hinge 14 center-point B, h
1for lower guide arm inner hinge 13 center-point A and outer spherical hinge 14 center-point B diff-Hs, l
1for lower guide arm brachium.
Step 2.2, set up zero load guide arm length analytic model at present;
(y
1-Δy
1)
2+(h
1+h-Δz
1)
2＝l
1 2 (2)
Wherein: y
1, h
1, l
1with (1), y
1for the Y-direction relative distance of the 13 center-point A of guide arm inner hinge under fully laden and outer spherical hinge 14 center-point B, h
1for lower guide arm inner hinge 13 center-point A and outer spherical hinge 14 center-point B diff-Hs, l
1for lower guide arm brachium.Δ y
1for be fully loaded with light condition at present the outer spherical hinge 14 center-point B of guide arm to the Y-direction variation distance of B ', Δ z
1for be fully loaded with light condition at present the outer spherical hinge 14 center-point B of guide arm to the Z-direction of B ', change distance, h jumping amount on vehicle body when being fully loaded with light condition, be namely fully loaded with light condition at present guide arm inner hinge 13 center-point A to the Z-direction variation distance of A '.
By Fig. 5 solid line AB, be partly lower guide arm 11 fully ladens, lower guide arm brachium l
1to Y-axis, Z axis projection, obtain Y-axis projection length of side y respectively
1, inside and outside hinge center-point diff-H h
1(mm) be the Z axis projection length of side.So, projection length of side y
1(mm), h
1(mm) together with lower guide arm brachium l
1form a right-angled triangle AOB, and meet Pythagorean theorem geometric relationship, just can build one and contain two known variables l
1, y
1equation (1).
By step 1.5,1.6, determined the inside and outside spherical hinge center position variable quantity of lower guide arm 11 that is fully loaded with zero load, be that under at full load, guide arm inner hinge center A point arrives zero load guide arm inner hinge center A ' at present along jumping h (mm) in Z-direction, under at full load, the outer spherical hinge center B point of guide arm is respectively along Y-axis, Z axis changes delta y
1(mm), Δ z
1(mm), arrive the zero load outer spherical hinge center B ' of guide arm at present.
In this embodiment, with graphics software, carry measuring tool and measure the outer spherical hinge 14 center-point B of lower guide arm in Y, Z direction projection variation distance, measure Δ y
1(mm), Δ z
1(mm);
By step 1.6, on vehicle body, jumping amount h (mm) is designing requirement amount, according to different vehicles, should maintain certain limit, is generally 50mm left and right, can be made as known constant.
If Fig. 5 dotted line A ' B ' part is lower guide arm 11 light conditions, due to the constant constraint of guide arm brachium, zero load is guide arm brachium l at present
1(mm), based on hinge center position variation relation, more respectively to Y-axis, Z axis projection, the projection length of side is changed to respectively y
1-Δ y
1(mm), h
1+ h-Δ z
1(mm), the projection length of side is together with lower guide arm brachium l
1(mm) form a right-angled triangle A ' O ' B ', and meet Pythagorean theorem geometric relationship, also can build one and contain two known variables l
1, y
1equation (2).
By step 1.3, lower guide arm 11 two ends hinge center-point diff-H h
1(mm) be Known designs required amount.So (1), (2) equation can go out lower guide arm brachium l by simultaneous solution
1.
Step 2.3, set up guide arm length analytic model at full load;
y
2 2+h
2 2＝l
2 2 (3)
Wherein: y
2for the Y-direction relative distance of the 7 center-point D of guide arm inner hinge on fully laden and outer spherical hinge 3 center-point C, h
2for upper guide arm inner hinge 7 center-point D and outer spherical hinge 3 center-point C diff-Hs, l
2for upper guide arm brachium.
Upper guide arm length analytic model when step 2.4, foundation zero load;
(y
2+Δy
2)
2+(h
2-h+Δz
2)
2＝l
2 2 (4)
Wherein: y
2, h
2, l
2with (3), y
2for the Y-direction relative distance of the 7 center-point D of guide arm inner hinge on fully laden and outer spherical hinge 3 center-point C, h
2for upper guide arm inner hinge 7 center-point D and outer spherical hinge 3 center-point C diff-Hs, l
2for upper guide arm brachium.Δ y
2the outer spherical hinge 3 center-point C of upper guide arm are to the Y-direction variation distance of C ', Δ z when being fully loaded with light condition
2the outer spherical hinge 3 center-point C of upper guide arm change distance to the Z-direction of C ' when being fully loaded with light condition, h jumping amount on vehicle body when being fully loaded with light condition, while being namely fully loaded with light condition above guide arm inner hinge 7 center-point D to the Z-direction variation distance of D '.
By Fig. 6 solid line CD, be partly upper guide arm 4 fully ladens, upper guide arm brachium l
2to Y-axis, Z axis projection, obtain Y-axis projection length of side y respectively
2, inside and outside hinge center-point diff-H h
2(mm) be the Z axis projection length of side.So, projection length of side y
2(mm), h
2(mm) together with upper guide arm brachium l
2form a right-angled triangle CPD, and meet Pythagorean theorem geometric relationship, just can build one and contain two known variables l
2, y
2equation (3).
By step 1.5,1.6, determined spherical hinge center variable quantity inside and outside the upper guide arm be fully loaded with zero load, be that at full load, guide arm inner hinge center D point is gone up guide arm inner hinge center D ' along jumping in Z-direction when h (mm) arrives zero load, at full load, the outer spherical hinge center C point of guide arm is respectively along Y-axis, Z axis changes delta y
1(mm), Δ z
1(mm) the outer spherical hinge center C of upper guide arm while, arriving zero load '.
In this embodiment, with graphics software, carry measuring tool and measure the outer spherical hinge center-point 3 of upper guide arm in Y, Z direction projection variation distance, measure Δ y
2(mm), Δ z
2(mm), on vehicle body, jumping amount h (mm) is known.
If Fig. 6 dotted line C ' D ' part is upper guide arm 4 light conditions, due to the constant constraint of guide arm brachium, upper guide arm brachium l when unloaded
2(mm), the hinge center position variation relation based on step 2.5, more respectively to Y-axis, Z axis projection, the projection length of side is changed to respectively y
2+ Δ y
2(mm), h
2-h+ Δ z
2(mm), the projection length of side is together with upper guide arm brachium l
2(mm) form a right-angled triangle C ' P ' D ', and meet Pythagorean theorem geometric relationship, also can build one and contain two known variables l
2, y
2equation (4).
By step 1.3, upper guide arm 4 two ends hinge center-point diff-H h
2(mm) be Known designs required amount.(3), (4) equation can go out upper guide arm brachium by simultaneous solution.
Below with reference to accompanying drawing, introduce an example calculation, its parameter value comes from certain electronic guide to visitors car.Take and be fully loaded with as initial condition, just fixed as the wheel alignment parameter of following table and structural arrangement parameter, emulation when being fully loaded with light condition, variations such as jumping on control vehicle body, camber angle and wheelspan, and simplified structural modal is to geometric model.Here only need be in Geometric Modeling environment, with software carry measuring tool measure guide arm inside and outside spherical hinge center-point at Y, Z direction projection, change distance, measure Δ y
2(mm) be-2.9806 (upper guide arm Y-direction projected length diminishes), Δ z
2(mm) be 1.156, Δ y
1(mm) be 7.0031, Δ z
1(mm) be 0.6264; Substitution analytic equation (1), (2), (3) and (4), just can calculate guide arm brachium.Detail parameters and the results are shown in following table 1:
Table 1 suspension geometry parameter and brachium result table
Although at length disclose the present invention with reference to accompanying drawing, it should be understood that these descriptions are only exemplary, be not used for limiting application of the present invention.Protection scope of the present invention is limited by accessory claim, and can be included in various modification, remodeling and the equivalents of doing for invention in the situation that does not depart from protection domain of the present invention and spirit.
Claims (1)
1. guide arm and a lower guide arm length calculation method on double cross arm independent suspension, is characterized in that:
Step 1, sets up YOZ system of axes, and Y coordinate axle is camber angle wheel axis while being 0 °, outwards for just; Z coordinate axle is the plumb bob vertical of crossing on vehicle body center buttock in wheel axis lengthwise position, upwards for just; In this system of axes, build respectively plane geometry model fully loaded and that light condition double cross arm independent suspension is simplified, it is realized in the following manner:
Step 1.1, double cross arm independent suspension suspension is carried out to geometry simplify;
Under under step 1.2, fully laden, determine outer spherical hinge (3) the center-point C of upper guide arm, the position of outer spherical hinge (14) the center-point B of lower guide arm;
Under step 1.3, fully laden, determine the Z-direction position of upper guide arm inner hinge (7) center-point D, lower guide arm inner hinge (13) center-point A, and suppose their Y-direction position;
Outer spherical hinge (3) the center-point C of upper guide arm that step 1.4, utilization are determined and outer spherical hinge (14) the center-point B of lower guide arm, and upper guide arm inner hinge (7) the center-point D of hypothesis and the position of lower guide arm inner hinge (13) center-point A, set up fully laden suspension geometry model;
Step 1.5, from being fully loaded with to light condition, determine outer spherical hinge (3) the center-point C ' of upper guide arm, the position of outer spherical hinge (14) the center-point B ' of lower guide arm;
Step 1.6, from being fully loaded with to light condition, determine upper guide arm inner hinge (7) center-point C ', the Z-direction change location of lower guide arm inner hinge 13 center-point B ';
Step 1.7, utilize the position of outer spherical hinge (3) the center-point C ' of upper guide arm of definite light condition, lower guide arm outer spherical hinge (14) center-point B ', upper guide arm inner hinge (7) center-point D ', lower guide arm inner hinge (13) center-point A ', set up light condition suspension geometry model;
Step 2, by under the fully loaded and light condition of determining, the geometric relationship of upper guide arm and lower guide arm, sets up analytic geometry model, calculates guide arm and lower guide arm brachium; It is realized in the following manner:
Step 2.1, set up under fully laden lower guide arm length analytic model;
y
1 2+h
1 2＝l
1 2 (1)
Wherein: y
1for the Y-direction relative distance of guide arm inner hinge (13) center-point A under fully laden and outer spherical hinge (14) center-point B, h
1for lower guide arm inner hinge (13) center-point A and outer spherical hinge (14) center-point B diff-H, l
1for lower guide arm length;
Step 2.2, set up zero load guide arm length analytic model at present;
(y
1-Δy
1)
2+(h
1+h-Δz
1)
2＝l
1 2 (2)
Wherein: y
1for the Y-direction relative distance of guide arm inner hinge (13) center-point A under fully laden and outer spherical hinge (14) center-point B, h
1for lower guide arm inner hinge (13) center-point A and outer spherical hinge (14) center-point B diff-H, l
1for lower guide arm length; Δ y
1for be fully loaded with light condition at present outer spherical hinge (14) the center-point B of guide arm to the Y-direction variation distance of B ', Δ z
1for be fully loaded with light condition at present outer spherical hinge (14) the center-point B of guide arm to the Z-direction of B ', change distance, h for be fully loaded with light condition at present guide arm inner hinge (13) center-point A to the Z-direction variation distance of A ';
Due to Δ y
1(mm), Δ z
1(mm) by measuring acquisition, h in geometric model
1, h is known quantity, by equation (1) and (2), calculates two known variables l
2, y
2value, thereby obtain lower guide arm length;
Step 2.3, set up guide arm length analytic model at full load;
y
2 2+h
2 2＝l
2 2 (3)
Wherein: y
2for the Y-direction relative distance of upper guide arm inner hinge (7) center-point D and outer spherical hinge (3) center-point C under fully laden, h
2for upper guide arm inner hinge (7) center-point D and outer spherical hinge (3) center-point C diff-H, l
2for upper guide arm brachium;
Upper guide arm length analytic model when step 2.4, foundation zero load;
(y
2+Δy
2)
2+(h
2-h+Δz
2)
2＝l
2 2 (4)
Wherein: y
2for the Y-direction relative distance of upper guide arm inner hinge (7) center-point D and outer spherical hinge (3) center-point C under fully laden, h
2for upper guide arm inner hinge (7) center-point D and outer spherical hinge (3) center-point C diff-H, l
2upper guide arm brachium, Δ y
2outer spherical hinge (3) the center-point C of upper guide arm is to the Y-direction variation distance of C ', Δ z when being fully loaded with light condition
2outer spherical hinge (3) the center-point C of upper guide arm changes distance to the Z-direction of C ' when being fully loaded with light condition, h when being fully loaded with light condition upper guide arm inner hinge (7) center-point D to the Z-direction variation distance of D ';
Due to Δ y
2(mm), Δ z
2(mm) by measuring acquisition, h in geometric model
2, h is known quantity, by equation (3) and (4), calculates two known variables l
2, y
2value, thereby obtain guide arm length.
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