CN106777605B - Suspension side-view geometric motion analysis method and system - Google Patents
Suspension side-view geometric motion analysis method and system Download PDFInfo
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Abstract
The embodiment of the invention provides a suspension side-view geometric motion analysis method and system. The suspension side view geometric motion analysis method and the suspension side view geometric motion analysis system simplify the suspension from a three-dimensional space to a two-dimensional plane for analysis and calculation, simplify the calculation process, shorten the calculation time and facilitate the practical application of engineering. The suspension side-looking geometric motion analysis method and the system meet the calculation precision requirement of general side-looking geometric performance parameters and can be used for early design and parameter optimization of the suspension of the type.
Description
Technical Field
The invention relates to the technical field of analysis and measurement control of automobiles, in particular to a suspension side-view geometric motion analysis method and system.
Background
In the initial development process of vehicle type products, the geometric motion analysis of a suspension is an important theoretical basis for the design of a suspension system. The geometrical motion analysis of the suspension can solve a kinematic model of the suspension, and simultaneously can determine geometrical parameters and a change rule of a suspension mechanism. The geometrical motion analysis of the suspension is the basis for analyzing the influence of the geometrical arrangement of the suspension and the parameters of a suspension system on the performance of the automobile. Due to the complexity of the automobile suspension structure, mathematical methods such as multi-body dynamics are generally adopted to analyze the automobile suspension structure, and the analysis method is high in calculation difficulty, long in calculation time and inconvenient for practical application of engineering.
Disclosure of Invention
In order to solve the above technical problems, embodiments of the present invention provide a suspension side view geometric motion analysis method and system. The suspension side view geometric motion analysis method and the suspension side view geometric motion analysis system simplify the suspension from a three-dimensional space to a two-dimensional plane for analysis and calculation, simplify the calculation process, shorten the calculation time and facilitate the practical application of engineering. The suspension side-looking geometric motion analysis method and the system meet the calculation precision requirement of general side-looking geometric performance parameters and can be used for early design and parameter optimization of the suspension of the type.
According to an aspect of an embodiment of the present invention, there is provided a suspension side view geometric motion analysis method, including:
reading hard point information of a suspension, wherein the hard point information of the suspension comprises: front axle hard spot information and rear axle hard spot information;
converting the hard point information of the suspension under the three-dimensional coordinate system into a rod system coordinate value on a two-dimensional plane; the rod system coordinate values of the suspension include: a front axle system coordinate value and a rear axle system coordinate value;
according to the coordinate values of the front axle system and the rear axle system, performing front-rear axle IC calculation to respectively obtain virtual hinge center IC of the front axleFAnd virtual hinge center IC of rear axleR；
Selecting an analysis type, wherein the analysis type is a braking working condition or an acceleration working condition;
from the virtual hinge centre IC of the front axleFAnd virtual hinge center IC of rear axleRAnd (5) performing suspension side view geometric motion analysis.
Alternatively, the virtual hinge center IC is obtained according to the obtained front axleFAnd virtual hinge center IC of rear axleRPerforming suspension side view geometric motion analysis, comprising:
if the analysis type is the braking working condition, selecting a braking form, wherein the braking form is internal braking or external braking;
the braking mode is that when the external braking is performed, the virtual hinge center IC is based on the front axleFGeometric calculation is carried out to obtain the front axle side view virtual arm length lsvsa,FAngle phi with first front-axis side view virtual armF(ii) a Virtual hinge center IC according to rear axleRGeometric calculation is carried out to obtain the rear axle side view virtual arm length lsvsa,RAnd a second rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate;
the braking mode is that when the internal braking is performed, the virtual hinge center IC is based on the front axleFBefore calculation is obtainedAxial side view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRRespectively calculating to obtain the rear axle side view virtual arm length lsvsa,RAngle theta with second rear axle side view virtual armR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate;
if the analysis type is the acceleration working condition, selecting a rear axle form; wherein the rear axle is in the form of a rigid axle or independent suspension;
when the rear axle is in the form of said rigid axle, according to the virtual articulation center IC of the front axleFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRCalculating to obtain the rear axle side view virtual arm length lsvsa,RAnd a second rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: the front axle forward pitch resistance and the rear axle squat resistance;
according to the virtual centre of articulation IC of the front axle when the rear axle is in the form of an independent suspensionFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRRespectively calculating to obtain the rear axle side view virtual arm length lsvsa,RAngle theta with second rear axle side view virtual armR(ii) a And further calculating to obtain performance parameters: front axle pitch resistance and rear axle squat resistance.
Optionally, the front axle coordinate value includes an upper swing arm first point U1FThe second point U of the upper swing arm2FFirst point L of lower swing arm1FSecond point L of lower swing arm2FFront axle wheel center W1And the tangent point P of the front axle rim and the ground1The coordinate values of the bar system; virtual hinge center IC of front axleFIs a swing arm U on the front shaft1FU2FAnd a lower swing arm L of the front axle1FL2FThe intersection point of (a).
Optionally, the rear axle coordinate value comprises an upper swing arm third point U1RAnd the fourth point U of the upper swing arm2RA third point L of the lower swing arm1RFourth point L of lower swing arm2RAnd a rear axle hub W2And the tangent point P of the rear axle wheel rim and the ground2The coordinate values of the bar system; virtual hinge center IC of rear axleRIs a swing arm U on a rear shaft1RU2RAnd a lower swing arm L of the rear axle1RL2RThe intersection point of (a).
Optionally, the first front-axis side view virtual arm angle phiFVirtual hinge center IC with front axleFAnd the tangent point P1 of the front axle rim with the ground; the first rear axle side view virtual arm included angle phiRVirtual hinge center IC with rear axleRAnd the tangent point P2 of the rear axle rim to the ground.
Optionally, when the braking form is external braking, the front axle anti-nodding rate and the braking force distribution coefficient p of the front axleb,FThe first side of the front axle looks at the virtual arm included angle phiFThe wheelbase l is related to the height h of the mass center; rear axle lift resistance and rear axle brake force distribution coefficient pb,RFirst rear axle side view virtual arm included angle phiRThe wheelbase l and the centroid height h.
Optionally, the second front-axis side view virtual arm angle θFVirtual hinge center IC with front axleFAnd a wheel center W1Hard spot information of (1); the second rear axle side view virtual arm included angle thetaRVirtual hinge center IC with rear axleRAnd a wheel center W2Is related to the hard spot information.
Optionally, when the braking form is internal braking, the front axle anti-nodding rate and the braking force distribution coefficient p of the front axleb,FThe second front-axis side view virtual arm included angle thetaFThe wheelbase l is related to the height h of the mass center; rear axle lift resistance and rear axle brake force distribution coefficient pb,RSecond rear axle side view virtual arm included angle thetaRThe wheelbase l and the centroid height h.
Optionally, the front-axis forward-tilting resistance rate and the second front-axis side-view virtual arm included angle θ are set under the acceleration conditionFThe wheelbase l is related to the height h of the mass center; under the acceleration working condition and when the rear shaft is a rigid shaft, the squat resistance rate of the rear shaft and the side view virtual arm included angle phi of the first rear shaftRThe wheelbase l and the centroid height h.
Optionally, under and after acceleration conditionsWhen the axle is an independent suspension, the squat resistance of the rear axle and the included angle theta of the side view virtual arm of the second rear axleRThe wheelbase l and the centroid height h.
In another aspect, a suspension side view geometric motion analysis system is provided, including:
a reading module for reading hard point information of a suspension, wherein the hard point information of the suspension comprises: front axle hard spot information and rear axle hard spot information;
the conversion module is used for converting the hard point information of the suspension under the three-dimensional coordinate system into a rod system coordinate value on a two-dimensional plane; the rod system coordinate values of the suspension include: a front axle system coordinate value and a rear axle system coordinate value;
a calculation module for calculating front and rear axle IC according to the coordinate value of the front axle rod system to obtain virtual hinge center IC of the front axleFAnd virtual hinge center IC of rear axleR；
The selection module is used for selecting an analysis type, wherein the analysis type is a braking working condition or an acceleration working condition;
an analysis module for obtaining a virtual articulation center IC of the front axleFAnd virtual hinge center IC of rear axleRAnd (5) performing suspension side view geometric motion analysis.
Optionally, the analysis module is further configured to:
under the braking working condition, when the braking form is external braking, according to the virtual hinge center IC of the front axleFGeometric calculation is carried out to obtain the front axle side view virtual arm length lsvsa,FAngle phi with first front-axis side view virtual armF(ii) a Virtual hinge center IC according to rear axleRGeometric calculation is carried out to obtain the rear axle side view virtual arm length lsvsa,RAnd a second rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate;
under the braking working condition, when the braking form is internal braking, according to the virtual hinge center IC of the front axleFAnd virtual hinge center IC of rear axleRRespectively calculating to obtain a second front-axis side-view virtual arm included angle thetaFAnd a second rear-axis side view virtual armIncluded angle thetaR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate;
under the acceleration condition, when the rear shaft is in the form of a rigid shaft, the virtual hinge center IC of the front shaft is usedFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRCalculating to obtain the rear axle side view virtual arm length lsvsa,RAnd a second rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: the front axle forward pitch resistance and the rear axle squat resistance;
according to the virtual center of articulation IC of the front axle when the rear axle is in the form of an independent suspension under said acceleration conditionsFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRRespectively calculating to obtain the rear axle side view virtual arm length lsvsa,RAngle theta with second rear axle side view virtual armR(ii) a And further calculating to obtain performance parameters: front axle pitch resistance and rear axle squat resistance.
The technical scheme of the invention has the following beneficial effects:
in the scheme, the suspension side view geometric motion analysis method and the suspension side view geometric motion analysis system simplify the suspension from a three-dimensional space to a two-dimensional plane for analysis and calculation, simplify the calculation process, shorten the calculation time and facilitate the practical application of engineering. The suspension side-looking geometric motion analysis method and the system meet the calculation precision requirement of general side-looking geometric performance parameters and can be used for early design and parameter optimization of the suspension of the type.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the description of the embodiments of the present invention will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art that other drawings can be obtained based on these drawings without creative efforts.
Fig. 1 is a schematic flow chart of a suspension side view geometric motion analysis method according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a double wishbone suspension model according to an embodiment of the present invention;
FIG. 3 is a simplified model diagram of a side view geometry calculation according to an embodiment of the present invention;
FIG. 4 is a diagrammatic view of a virtual hinge center IC in accordance with an embodiment of the present invention;
FIG. 5 is a side view geometry of an external brake application provided in accordance with an embodiment of the present invention;
FIG. 6 is a side view geometry of the inner brake of the present invention;
FIG. 7 is a side view geometry schematic of a rigid rear axle in an acceleration condition according to an embodiment of the present invention;
FIG. 8 is a side view geometry schematic of a rear axle independent suspension for an acceleration condition in accordance with an embodiment of the present invention;
FIG. 9 is a schematic flow chart of a suspension side view geometric motion analysis system according to an embodiment of the present invention;
fig. 10 is a block diagram of a suspension side view geometry analysis process according to an embodiment of the present invention.
Detailed Description
In order to make the technical problems, technical solutions and advantages of the present invention more apparent, the following detailed description is given with reference to the accompanying drawings and specific embodiments.
Fig. 1 is a flowchart of a suspension side view geometric motion analysis method according to an embodiment of the present invention.
As shown in fig. 1, the suspension side view geometric motion analysis method includes the following steps:
The hard point is a point which has fixed three-dimensional coordinate position and can not move in the automobile modeling process. The hard point information of the suspension refers to the coordinates of the important part of the suspension in a vehicle body coordinate system. The important parts are the front axle and the rear axle in this embodiment.
Fig. 2 is a double wishbone suspension model according to an embodiment of the present invention. As shown in fig. 2, a double wishbone suspension model includes: an upper cross arm 1, a lower cross arm 2 and wheels 3.
Simplifying both front and rear axles of the suspension into the double wishbone suspension model, comprising: the suspension model comprises a front axle double-wishbone suspension model and a rear axle double-wishbone suspension model.
102, converting hard point information of a suspension under a three-dimensional coordinate system into a rod system coordinate value on a two-dimensional plane; the rod system coordinate values of the suspension include: front axle coordinate values and rear axle coordinate values.
Fig. 3 is a simplified model of side view geometry calculation, i.e., a three-dimensional model of the double wishbone suspension shown in fig. 2 is converted into a simplified model of the linkage system shown in fig. 3 for side view geometry calculation. And respectively converting the double-wishbone suspension models of the front axle and the rear axle of the suspension into rod system simplified models of the front axle and the rear axle, and further acquiring the rod system coordinate values of the front axle and the rear axle.
Wherein the front axle coordinate value comprises a first point U of the upper swing arm1FThe second point U of the upper swing arm2FFirst point L of lower swing arm1FSecond point L of lower swing arm2FFront axle wheel center W1And the tangent point P of the front axle rim and the ground1The coordinate values of the bar system.
The coordinate value of the rear shaft lever system comprises a third point U of the upper swing arm1RAnd the fourth point U of the upper swing arm2RA third point L of the lower swing arm1RFourth point L of lower swing arm2RAnd a rear axle hub W2And the tangent point P of the rear axle wheel rim and the ground2The coordinate values of the bar system.
103, according to the coordinate values of the front shaft system and the rear shaft system, calculating the virtual hinge center IC of the front shaft and the virtual hinge center IC of the rear shaft, and respectively obtaining the virtual hinge center IC of the front shaft through calculationFAnd virtual hinge center IC of rear axleR。
FIG. 4 is a diagrammatic illustration of a virtual hinge center IC, with the upper swing arm U1U2And a lower swing arm L1L2And extending to intersect, wherein the intersection point is the virtual hinge center IC.
From the above theory, it can be seen that the virtual hinge center IC of the front axleFIs a swing arm U on the front shaft1FU2FAnd a lower swing arm L of the front axle1FL2FThe intersection point of (a);
virtual hinge center IC of rear axleRIs a swing arm U on a rear shaft1RU2RAnd a lower swing arm L of the rear axle1RL2RThe intersection point of (a).
And 104, selecting an analysis type, wherein the analysis type is a braking working condition or an acceleration working condition.
1) And if the analysis type is the braking working condition, selecting a braking form, wherein the braking form is internal braking or external braking.
The braking mode is that when the external braking is performed, the virtual hinge center IC is based on the front axleFGeometric calculation is carried out to obtain the front axle side view virtual arm length lsvsa,FAngle phi with first front-axis side view virtual armF；
Wherein the first front-axis side-view virtual arm included angle phiFVirtual hinge center IC with front axleFAnd the tangent point P of the front axle rim and the ground1It is related.
Referring to fig. 5, a virtual hinge center IC of the front axleFAnd the tangent point P of the front axle rim and the ground1Are connected into a straight line, and the included angle between the straight line and the ground is the included angle phi of the first front-axis side-view virtual armF(ii) a Front axle side view virtual arm length lsvsa,FI.e. the virtual hinge center IC of the front axleFTo pass through the wheel center W1Is measured.
Performing geometric calculation according to the virtual hinge center ICR of the rear axle to obtain the side view virtual arm length l of the rear axlesvsa,RAnd a second rear axle side view virtual arm included angle phiR。
The first rear axle side view virtual arm included angle phiRVirtual hinge center IC with rear axleRAnd the tangent point P of the rear axle wheel rim and the ground2It is related.
With reference to figure 5 of the drawings,virtual hinge center IC of rear axleRAnd the tangent point P of the rear axle wheel rim and the ground2Are connected into a straight line, and the included angle between the straight line and the ground is the included angle phi of the virtual arm viewed from the side of the first rear axleR(ii) a Rear axle side view virtual arm length lsvsa,RI.e. the virtual hinge center IC of the rear axleRTo pass through the wheel center W2Is measured.
And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate;
wherein the front axle anti-nodding rate and the front axle braking force distribution coefficient pb,FThe first side of the front axle looks at the virtual arm included angle phiFThe wheelbase l is related to the height h of the mass center; the wheel base l is the distance between the front axle and the rear axle, the height h of the center of mass is the height from the center of mass of the suspension to the ground, and both the wheel base l and the height h of the center of mass are constants.
The front axle anti-nodding rate is expressed as
anti-diveF＝pb,F·tan(φF)·l/h (1)
Wherein, anti-diveFRepresenting the front axis nodding resistance rate.
The anti-lift rate of the rear axle and the brake force distribution coefficient p of the rear axleb,RFirst rear axle side view virtual arm included angle phiRThe wheelbase l and the centroid height h.
The rear axle lift resistance is related to
anti-liftR＝pb,R·tan(φR)·l/h (2)
Wherein, anti-liftRIndicating the rear axle anti-lift ratio.
The front axle anti-nodding rate when the braking form is the external braking can be obtained through the formula (1);
the rear axle lift resistance at the time of braking in the form of the external braking can be obtained by the equation (2).
If the braking mode is the internal braking, according to the virtual hinge center IC of the front axleFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRRespectively calculating to obtain the rear axle side view virtual arm lengthlsvsa,RAngle theta with second rear axle side view virtual armR(ii) a To avoid repetition, the front axle side view virtual arm length lsvsa,FAnd rear axial side view virtual arm length lsvsa,RThe detailed method is not described again.
Wherein the second front-axis side view virtual arm included angle thetaFVirtual hinge center IC with front axleFAnd a wheel center W1Is related to the hard spot information.
Referring to fig. 6, a virtual hinge center IC of the front axleFAnd a wheel center W1Connected in a straight line and passes through the wheel center W1Parallel lines for making the ground, the parallel lines and the linear ICFW1The included angle between the two is a second front-axis side-view virtual arm included angle thetaF。
The second rear axle side view virtual arm included angle thetaRVirtual hinge center IC with rear axleRAnd a wheel center W2Is related to the hard spot information.
Referring to fig. 6, a virtual hinge center IC of the rear axleRAnd a wheel center W2Connected in a straight line and passes through the wheel center W2Parallel lines for making the ground, the parallel lines and the linear ICRW2The included angle between the two is a second rear-axis side-view virtual arm included angle thetaR。
According to the calculated second front-axis side-view virtual arm included angle thetaFAngle theta with second rear axle side view virtual armRCalculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate.
The braking form is that when the internal braking is carried out, the front axle anti-nodding rate and the braking force distribution coefficient p of the front axleb,FThe second front-axis side view virtual arm included angle thetaFThe wheelbase l and the centroid height h.
The front axle anti-nodding rate is expressed by
The braking form is that when the internal braking is carried out, the anti-lifting rate of the rear axle and the braking force distribution coefficient p of the rear axleb,RSecond rear axle side view virtual arm included angle thetaRThe wheelbase l and the centroid height h.
The lift rate of the rear axle is expressed by
The front axle anti-nodding rate when the braking form is the internal braking can be obtained through the formula (3);
the rear axle lift resistance at the time of the internal braking can be obtained by the equation (4).
2) If the analysis type is the acceleration working condition, selecting a rear axle form; wherein the rear axle is in the form of a rigid axle or independent suspension.
When the rear axle is in the form of said rigid axle, see fig. 7, according to the virtual centre of articulation IC of the front axleFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a To avoid repetition, the specific method is not described in detail.
When the rear axle is in the form of said rigid axle, see fig. 7, according to the virtual hinge centre IC of the rear axleRCalculating to obtain the rear axle side view virtual arm length lsvsa,RAnd a second rear axle side view virtual arm included angle phiR(ii) a To avoid repetition, the specific method is not described in detail.
And further calculating to obtain performance parameters: front axle pitch resistance and rear axle squat resistance.
Under the acceleration working condition, the included angle theta between the front-axis forward-elevation resisting rate and the second front-axis side-looking virtual armFThe wheelbase l and the centroid height h.
The front shaft forward pitch resistance is expressed by
anti-liftF＝tan(θF)·l/h (5)
Wherein, anti-liftFIndicating the front axle anti-pitch rate.
Under the acceleration working condition and when the rear shaft is a rigid shaft, the squat resistance rate of the rear shaft and the side view virtual arm included angle phi of the first rear shaftRThe wheelbase l and the centroid height h.
The squat resistance of the rear axle is expressed by
anti-squatR＝tan(φR)·l/h (6)
Wherein, anti-squatRIndicating the squat resistance of the rear axle.
The front axle pitch resistance rate when the rear axle is a rigid axle can be obtained through the formula (5);
the squat resistance of the rear axle when the rear axle is a rigid axle can be obtained by equation (6).
When the rear axle is in the form of an independent suspension, see fig. 8, according to the virtual center of articulation IC of the front axleFCalculating to obtain the front-axle side-view virtual arm length lsvsa,，FAnd a second front-axis side view virtual arm angle thetaF(ii) a To avoid repetition, the specific method is not described in detail.
When the rear axle is in the form of an independent suspension, see fig. 8, according to the virtual center of articulation IC of the rear axleRRespectively calculating to obtain the rear axle side view virtual arm length lsvsa,RAngle theta with second rear axle side view virtual armR(ii) a To avoid repetition, the specific method is not described in detail.
And further calculating to obtain performance parameters: front axle pitch resistance and rear axle squat resistance.
Under the acceleration working condition and when the rear axle is an independent suspension, the squat resistance rate of the rear axle and the side view virtual arm included angle theta of the second rear axleRThe wheelbase l and the centroid height h.
The squat resistance of the rear axle is expressed by
anti-squatR＝tan(θR)·l/h (7)
The front axle anti-pitching rate when the rear axle is an independent suspension can be obtained through the formula (5);
the squat resistance of the rear axle when the rear axle is an independent suspension can be obtained by equation (7).
The calculated performance parameters can be used as the basis for adjusting the corresponding hard points when the suspension is arranged. The design of the suspension system should minimize the front axle nodding amount and the rear axle lifting amount during braking and the front axle forward pitching amount and the rear axle squat amount during driving. That is, the front axle anti-nod rate during braking, the rear axle anti-lifting rate during braking, the front axle anti-pitching rate during driving and the rear axle anti-squat rate during driving are maximized. The ideal value of each performance parameter is 1-100%, and the longitudinal motion characteristic of the suspension is the best. However, ideal values are difficult to achieve in practice for a number of reasons and are therefore rarely used as a reference. Taking the anti-nodding rate as an example, the anti-nodding rate can reach 50 percent generally.
On the other hand, the embodiment of the invention also provides a suspension side view geometric motion analysis system. Fig. 9 is a block diagram of a suspension side view geometric motion analysis system in accordance with an embodiment of the present invention.
As shown in fig. 9, the suspension side view geometric motion analysis system includes:
a reading module 901, configured to read hard point information of a suspension, where the hard point information of the suspension includes: front axle hard spot information and rear axle hard spot information;
a conversion module 902, configured to convert hard point information of a suspension in a three-dimensional coordinate system into a rod coordinate value on a two-dimensional plane; the rod system coordinate values of the suspension include: a front axle system coordinate value and a rear axle system coordinate value;
a calculating module 903, configured to perform front-rear axis IC calculation according to the coordinate values of the front axle system, and calculate to obtain virtual hinge centers IC of the front axles respectivelyFAnd virtual hinge center IC of rear axleR；
A selection module 904 for selecting an analysis type, the analysis type being a braking condition or an acceleration condition;
an analysis module 905 for obtaining a virtual articulation center IC of the front axleFAnd virtual hinge center IC of rear axleRAnd (5) performing suspension side view geometric motion analysis.
Optionally, the analysis module 905 is further configured to:
under the braking working condition, when the braking form is external braking, according to the virtual hinge center IC of the front axleFGeometric calculation is carried out to obtain the front axle side view virtual arm length lsvsa,FAngle phi with first front-axis side view virtual armF(ii) a Virtual hinge center IC according to rear axleRGeometric calculation is carried out to obtain the rear axle side view virtual arm length lsvsa,RAnd a second rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate.
Under the braking working condition, when the braking form is internal braking, according to the virtual hinge center IC of the front axleFAnd virtual hinge center IC of rear axleRRespectively calculating to obtain a second front-axis side-view virtual arm included angle thetaFAngle theta with second rear axle side view virtual armR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate.
Under the acceleration condition, when the rear shaft is in the form of a rigid shaft, the virtual hinge center IC of the front shaft is usedFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Under the acceleration condition, when the rear shaft is in the form of a rigid shaft, according to the virtual hinge center IC of the rear shaftRCalculating to obtain the rear axle side view virtual arm length lsvsa,RAnd a second rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: front axle pitch resistance and rear axle squat resistance.
According to the virtual center of articulation IC of the front axle when the rear axle is in the form of an independent suspension under said acceleration conditionsFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRRespectively calculating to obtain the rear axle side view virtual arm length lsvsa,RAngle theta with second rear axle side view virtual armR(ii) a And further calculating to obtain performance parameters: front axle pitch resistance and rear axle squat resistance.
The embodiment of the invention provides a suspension side-view geometric motion analysis method and system. With reference to fig. 10, the suspension side view geometric motion analysis method and system simplify the suspension from a three-dimensional space to a two-dimensional plane for analysis and calculation, simplify the calculation process, shorten the calculation time, and facilitate the practical application of engineering. The suspension side-looking geometric motion analysis method and the system meet the calculation precision requirement of general side-looking geometric performance parameters and can be used for early design and parameter optimization of the suspension of the type.
While the foregoing is directed to the preferred embodiment of the present invention, it will be understood by those skilled in the art that various changes and modifications may be made without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (10)
1. A suspension side view geometric motion analysis method is characterized by comprising the following steps:
reading hard point information of a suspension, wherein the hard point information of the suspension comprises: front axle hard spot information and rear axle hard spot information;
converting the hard point information of the suspension under the three-dimensional coordinate system into a rod system coordinate value on a two-dimensional plane; the rod system coordinate values of the suspension include: a front axle system coordinate value and a rear axle system coordinate value;
according to the coordinate values of the front shaft system and the rear shaft system, the front-rear shaft virtual hinge center IC is calculated to respectively obtain the virtual hinge center IC of the front shaftFAnd virtual hinge center IC of rear axleR；
Selecting an analysis type, wherein the analysis type is a braking working condition or an acceleration working condition;
from the virtual hinge centre IC of the front axleFAnd virtual hinge center IC of rear axleRPerforming suspension side view geometric motion analysis;
the virtual hinge center IC according to the obtained front axleFAnd virtual hinge center IC of rear axleRPerforming suspension side view geometric motion analysis, comprising:
if the analysis type is the braking working condition, selecting a braking form, wherein the braking form is internal braking or external braking;
the braking mode is that when the external braking is performed, the virtual hinge center IC is based on the front axleFGeometric calculation is carried out to obtain the front axle side view virtual arm length lsvsa,FAngle phi with first front-axis side view virtual armF(ii) a Virtual hinge center IC according to rear axleRGeometric calculation is carried out to obtain the rear axle side view virtual arm length lsvsa,RAnd a first rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate;
the braking mode is based on the virtual of the front axle when the internal braking is performedQuasi-hinge center ICFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRRespectively calculating to obtain the rear axle side view virtual arm length lsvsa,RAngle theta with second rear axle side view virtual armR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate;
if the analysis type is the acceleration working condition, selecting a rear axle form; wherein the rear axle is in the form of a rigid axle or independent suspension;
when the rear axle is in the form of said rigid axle, according to the virtual articulation center IC of the front axleFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRCalculating to obtain the rear axle side view virtual arm length lsvsa,RAnd a first rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: the front axle forward pitch resistance and the rear axle squat resistance;
according to the virtual centre of articulation IC of the front axle when the rear axle is in the form of an independent suspensionFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRCalculating to obtain the rear axle side view virtual arm length lsvsa,RAngle theta with second rear axle side view virtual armR(ii) a And further calculating to obtain performance parameters: front axle pitch resistance and rear axle squat resistance.
2. The method of claim 1, wherein the front axle coordinate values comprise an upper swing arm first point U1FThe second point U of the upper swing arm2FFirst point L of lower swing arm1FSecond point L of lower swing arm2FFront axle wheel center W1And the tangent point P of the front axle rim and the ground1The coordinate values of the bar system; virtual hinge center IC of front axleFIs a swing arm U on the front shaft1FU2FAnd a lower swing arm L of the front axle1FL2FThe intersection point of (a).
3. The method of claim 1, wherein the rear axle coordinate values comprise an upper swing arm third point U1RAnd the fourth point U of the upper swing arm2RA third point L of the lower swing arm1RFourth point L of lower swing arm2RAnd a rear axle hub W2And the tangent point P of the rear axle wheel rim and the ground2The coordinate values of the bar system; virtual hinge center IC of rear axleRIs a swing arm U on a rear shaft1RU2RAnd a lower swing arm L of the rear axle1RL2RThe intersection point of (a).
4. The method of analyzing suspension side view geometric motion of claim 1, wherein the first front side view virtual arm angle ΦFVirtual hinge center IC with front axleFAnd the tangent point P1 of the front axle rim with the ground; the first rear axle side view virtual arm included angle phiRVirtual hinge center IC with rear axleRAnd the tangent point P2 of the rear axle rim to the ground.
5. The method for analyzing the geometrical motion of the side view of the suspension according to claim 1 or 4, wherein when the braking mode is external braking, the front axle anti-nodding rate and the braking force distribution coefficient p of the front axle areb,FThe first side of the front axle looks at the virtual arm included angle phiFThe wheelbase l is related to the height h of the mass center; rear axle lift resistance and rear axle brake force distribution coefficient pb,RFirst rear axle side view virtual arm included angle phiRThe wheelbase l and the centroid height h.
6. The method of claim 1, wherein the second front-axis side-view virtual arm angle θ isFVirtual hinge center IC with front axleFAnd a wheel center W1Hard spot information of (1); the second rear axle side view virtual arm included angle thetaRVirtual hinge center IC with rear axleRAnd a wheel center W2Is related to the hard spot information.
7. The method of claim 1 or 6The suspension side view geometric motion analysis method is characterized in that when the braking form is internal braking, the front axle anti-nodding rate and the braking force distribution coefficient p of the front axleb,FThe second front-axis side view virtual arm included angle thetaFThe wheelbase l is related to the height h of the mass center; rear axle lift resistance and rear axle brake force distribution coefficient pb,RSecond rear axle side view virtual arm included angle thetaRThe wheelbase l and the centroid height h.
8. The method for analyzing the lateral geometrical motion of the suspension according to claim 1, wherein the front axle forward-tilting resistance rate and the second front axle lateral virtual arm included angle θ are determined under an acceleration conditionFThe wheelbase l is related to the height h of the mass center; under the acceleration working condition and when the rear shaft is a rigid shaft, the squat resistance rate of the rear shaft and the side view virtual arm included angle phi of the first rear shaftRThe wheelbase l and the centroid height h.
9. The method for analyzing the side-looking geometrical motion of the suspension fork of claim 1, wherein under an acceleration condition and when the rear axle is an independent suspension fork, the squat resistance of the rear axle and the side-looking virtual arm included angle θ of the second rear axleRThe wheelbase l and the centroid height h.
10. A suspension side view geometric motion analysis system, comprising:
a reading module for reading hard point information of a suspension, wherein the hard point information of the suspension comprises: front axle hard spot information and rear axle hard spot information;
the conversion module is used for converting the hard point information of the suspension under the three-dimensional coordinate system into a rod system coordinate value on a two-dimensional plane; the rod system coordinate values of the suspension include: a front axle system coordinate value and a rear axle system coordinate value;
a calculation module for calculating front and rear axle IC according to the coordinate value of the front axle rod system to obtain virtual hinge center IC of the front axleFAnd virtual hinge center IC of rear axleR；
The selection module is used for selecting an analysis type, wherein the analysis type is a braking working condition or an acceleration working condition;
an analysis module for obtaining a virtual articulation center IC of the front axleFAnd virtual hinge center IC of rear axleRPerforming suspension side view geometric motion analysis;
the analysis module is further to:
under the braking working condition, when the braking form is external braking, according to the virtual hinge center IC of the front axleFGeometric calculation is carried out to obtain the front axle side view virtual arm length lsvsa,FAngle phi with first front-axis side view virtual armF(ii) a Virtual hinge center IC according to rear axleRGeometric calculation is carried out to obtain the rear axle side view virtual arm length lsvsa,RAnd a first rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate;
under the braking working condition, when the braking form is internal braking, according to the virtual hinge center IC of the front axleFAnd virtual hinge center IC of rear axleRRespectively calculating to obtain a second front-axis side-view virtual arm included angle thetaFAngle theta with second rear axle side view virtual armR(ii) a And further calculating to obtain performance parameters: front axle anti-nodding rate and rear axle anti-lifting rate;
under the acceleration condition, when the rear shaft is in the form of a rigid shaft, the virtual hinge center IC of the front shaft is usedFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRCalculating to obtain the rear axle side view virtual arm length lsvsa,RAnd a first rear axle side view virtual arm included angle phiR(ii) a And further calculating to obtain performance parameters: the front axle forward pitch resistance and the rear axle squat resistance;
according to the virtual center of articulation IC of the front axle when the rear axle is in the form of an independent suspension under said acceleration conditionsFCalculating to obtain the front-axle side-view virtual arm length lsvsa,FAnd a second front-axis side view virtual arm angle thetaF(ii) a Virtual hinge center IC according to rear axleRRespectively calculating to obtain the rear axle side view virtual arm length lsvsa,RAngle theta with second rear axle side view virtual armR(ii) a And further calculating to obtain performance parameters: front axle damperForward pitch rate and squat resistance rate of the rear axle.
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