CN113239451B - Matlab program-based passenger car drive shaft arrangement checking method - Google Patents
Matlab program-based passenger car drive shaft arrangement checking method Download PDFInfo
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Abstract
The invention belongs to the technical field of vehicle manufacturing, and particularly relates to a passenger car drive shaft arrangement checking method based on a Matlab program. The method comprises the following steps: s1, establishing a mathematical model of limit values of inner node displacement and inner node rotation angle, and obtaining a value range of the length L of the driving shaft; s2, establishing a mathematical model of the limit value of the outer joint rotation angle, and correcting the value range of the length L of the driving shaft obtained in the step S1 according to the obtained limit value range of the included angle between the outer joint axis and the shaft lever; s3, establishing a mathematical model of the offset condition of the displacement of the inner joint bearing contact point, and correcting the value range of the length L of the driving shaft obtained in the step S2 according to the obtained limit value range of the displacement of the bearing contact point; s4, selecting an optimal solution of the length L of the driving shaft according to the result of the step S3. The invention has the characteristics of better calculation precision and effectively improving the arrangement checking efficiency of the driving shaft.
Description
Technical Field
The invention belongs to the technical field of vehicle manufacturing, and particularly relates to a passenger car drive shaft arrangement checking method based on a Matlab program.
Background
At present, in the process of arranging a power assembly of a passenger car with a front driving shaft, the position of the power assembly and the motion rule of a chassis piece are required to be considered to meet the motion requirement of the driving shaft. The main problems involved are the establishment of the pitch and the drive shaft axial length L. The feasibility analysis process of the traditional method is as follows:
after the position of the power assembly is determined, the theoretical inner nodes of the left and right driving shafts can be determined, the length L of the driving shafts is estimated by the theoretical inner nodes, the data of the initial edition driving shafts at a plurality of characteristic positions are completed through the L, the numerical values of the inner joint displacement, the rotation angle and the outer joint rotation angle are measured and are filled into a checking template, the possible ideal driving shaft length is estimated according to the distribution condition of each curve in the template, the L is corrected according to experience to obtain corrected length L1, the checking process is repeated, whether the L1 is an optimal solution is judged through the position of the characteristic curve in each limit value model in the template, if not ideal, the correction is continued to L2, the checking comparison is carried out, and the process is repeated until the optimal solution of the length is found, but the process usually needs to consume more energy and has low efficiency.
Therefore, it is necessary to design a method for checking the driving shaft arrangement of the passenger car, which has better calculation accuracy and can effectively improve the checking efficiency of the driving shaft arrangement.
For example, a method for checking the slip angle of the driving shaft and a system for checking the slip angle of the driving shaft described in the chinese patent application No. CN202010865995.3, the method for checking includes: acquiring a hard spot of the whole vehicle; acquiring the mass center position of the power assembly; acquiring adjustment parameter information of a suspension component; and acquiring a driving shaft checking model according to the hard spot of the whole vehicle, the mass center position and the adjustment parameter information, and acquiring a driving shaft enveloping body and a sliding swing angle curve according to the driving shaft checking model. While the displacement amount, four-wheel parameter adjustment amount and other influencing parameters of the power assembly are built in the driving shaft checking model, the contribution amount and the influence degree of each parameter variable to the driving shaft slip amount, the swing angle and the envelope can be effectively analyzed, meanwhile, specific analysis checking can be carried out by combining the actual whole vehicle arrangement and parameters, the problem of insufficient design or excessive design caused by the fact that all vehicle types are only checked by experience values is avoided, so that the obtained driving shaft envelope and slip swing angle curve are more accurate, but the defect is that the checking system mainly aims at checking the driving shaft slip deflection angle and cannot solve the problems of arrangement checking of the driving shaft and calculation of the optimal solution of the driving shaft length.
Disclosure of Invention
The invention provides a Matlab program-based passenger car drive shaft arrangement checking method which has better calculation accuracy and can effectively improve the drive shaft arrangement checking efficiency, and aims to solve the problem that in the prior art, in the process of arranging a passenger car power assembly with a front drive shaft, great effort is required to carry out arrangement checking on the drive shaft and calculation of the axial length of the drive shaft, so that the work efficiency is low.
In order to achieve the aim of the invention, the invention adopts the following technical scheme:
the passenger car driving shaft arrangement checking method based on Matlab program comprises the following steps:
s1, establishing a mathematical model of limit values of inner node displacement and inner node rotation angle, and obtaining a value range of the length L of a driving shaft;
s2, establishing a mathematical model of the limit value of the outer joint rotation angle, and correcting the value range of the length L of the driving shaft obtained in the step S1 according to the obtained limit value range of the included angle between the outer joint axis and the shaft rod;
s3, establishing a mathematical model of the offset condition of the displacement of the inner joint bearing contact point, and correcting the value range of the length L of the driving shaft obtained in the step S2 according to the obtained limit value range of the displacement of the bearing contact point;
s4, selecting an optimal solution of the length L of the driving shaft according to the result of the step S3.
Preferably, the step S1 includes the steps of:
establishing a coordinate system, wherein the abscissa is displacement, the ordinate is inner joint angle, sequentially connecting the points 1, 2, 3, 4 and 5 provided by a provider into a straight line to form a limit value mathematical model, and solving straight line equations of straight lines L1, L2 and L3 through the coordinates of the known points; the straight lines L1, L2 and L3 are obtained according to design experience;
let the theoretical inner node of the left drive shaft be O1, the actual inner node of the drive shaft be Ot, the outer node of the drive shaft be Mli, and any point on the outer node of the drive shaft be Mlo;
setting the axial length of a driving shaft, namely the distance between Mli and Ot, as L, taking a Mli MliH vertical O1Ot extension line as a point H, setting +.MliOtH=θ, and setting O1Ot=t, namely the inner joint rotation angle θ, wherein the displacement of an inner joint is t;
from the known spatial coordinate system where O1Ot is parallel to the y-axis and the coordinates of O1 (x 1, y1, z 1), mli (xi, yi, zi) and Mlo (xo, yo, zo), the spatial geometrical relationship is known that the coordinates of the H-point are (x 1, yi, z 1), and the parametric equations of t and θ are found:
let the straight line L equation be: θ=kt+b,
substituting the formula (1) and the formula (2) into the straight line L equation yields the following equation:
order the
Wherein f (L) represents a series of straight line groups, which are parallel to the model boundary straight line; l obtained by f (L) =0 is a boundary point.
Preferably, the step S1 further includes the steps of:
and f (L) is derived to obtain:
when k is less than 0, F' (L) is less than 0, and F (L) is a decreasing function; if the root of f (L) =0 is Lx3, substituting f (L) into coordinates (t, θ) corresponding to all points on the left side of the straight line L3, wherein f (L) < 0 is found, and the value range of L is L > Lx3;
when k is more than 0, since θ is less than 30 DEG, k is more than 0.1, L is more than 300 in engineering practice, it is obtained
That is, F' (L) is greater than 0, and F (L) is obtained as an increasing function; if k and b in the equations of the straight lines L1 and L2 are taken to be respectively substituted into the obtained roots of f (L) =0 to be Lxb and Lxb2, f (L) is substituted into the coordinates (t, θ) corresponding to all points on the right sides of the straight lines L1 and L2, and f (L) < 0 is found, and the value range of L is L < min (Lxb 1, lxb 2);
finally, the value range of L is Lx3 < L < min (Lxb, lxb 2).
Preferably, step S2 includes the steps of:
setting the swing angle of the outer joint of the driving shaft as phi, and meeting the requirement that phi is less than phi 0 The psi is 0 To permit the work swing angle, the coordinates of Ot are (x 1, y1-t, z 1) from step S1, and the vector angle ψ is found from the space vectors MliMlo and OtMli:
conversion according to formula (3) gives:
wherein |OtMli| in formula (3) is L; the range of L is obtained by using inequality (4).
Preferably, step S3 includes the steps of:
angular conversion displacement t θ =tan (θ) ×λ/2, λ being a coefficient of conversion determined by the structure of the inner joint of the drive shaft;
the geometrical relationship of the inner joint structure of the driving shaft is as follows:
when the angular conversion displacement is greater than 0, the bearing contact point displacement t z ＝t+t θ ；
When the angular conversion displacement is smaller than 0, the bearing contact point displacement t z ＝t-t θ ；
If the design requires t z Should be at t m And t n Let t be z >t m And t is z <t n ；
According to the design requirement t z Selecting the value range of L meeting the requirement.
Preferably, the straight lines L1, L2, L3 in the step S1 form a safety boundary, and the point coordinates (t, θ) of the inner joint of the driving shaft during the sliding process of each working condition are all within the safety boundary.
Preferably, the outer joint swing angle ψ of the driving shaft is the included angle between the outer joint axis and the driving shaft rod axis, and Xu Yonggong is the swing angle ψ 0 The value of (2) is 50 deg..
Preferably, the bearing contact point displacement t z The displacement t converted from the inner joint displacement t and the inner joint rotation angle θ Calculated to obtain t z The range of the value of (C) is-20 mm to +20mm.
Compared with the prior art, the invention has the beneficial effects that: according to the checking method, three mathematical models are established according to the spatial motion rule of the driving shaft: the inner node displacement and inner node corner mathematical model, outer node corner mathematical model and bearing contact point displacement mathematical model can accurately calculate the value range of the length of the driving shaft at one time according to the coordinates of some points in the known three-dimensional data of the mathematical model, and compared with the traditional checking process, the working efficiency is remarkably improved, and the method has more obvious advantages and significance in the whole vehicle modularized design process.
Drawings
FIG. 1 is a schematic representation of a mathematical model of the limits of inner node displacement and inner node rotation angle of the present invention;
FIG. 2 is a schematic representation of a mathematical model of the limits of outer joint angles in accordance with the present invention;
FIG. 3 is a schematic view of a drive shaft according to the present invention;
FIG. 4 is a schematic diagram of a main interface of the optimization design procedure of the driving shaft axial length parameter in the embodiment 1 of the present invention;
FIG. 5 is a schematic diagram of a main interface of the optimization design program for the fixed parameter of the driving shaft in the practical application process in embodiment 1 of the present invention;
FIG. 6 is a graph of the output effect of a feature value in FIG. 5 when the middle value of the range of values of the left drive shaft length is 450 mm;
FIG. 7 is a graph of the output effect of a feature value in FIG. 5 when the middle value of the range of values of the left drive shaft length is 452 mm;
fig. 8 is a characteristic value output effect diagram when the middle value of the range of values of the right drive shaft length is 361mm in fig. 5.
Detailed Description
In order to more clearly illustrate the embodiments of the present invention, specific embodiments of the present invention will be described below with reference to the accompanying drawings. It is evident that the drawings in the following description are only examples of the invention, from which other drawings and other embodiments can be obtained by a person skilled in the art without inventive effort.
Example 1:
the passenger car driving shaft arrangement checking method based on Matlab program comprises the following steps:
s1, establishing a mathematical model of limit values of inner node displacement and inner node rotation angle, and obtaining a value range of the length L of a driving shaft;
s2, establishing a mathematical model of the limit value of the outer joint rotation angle, and correcting the value range of the length L of the driving shaft obtained in the step S1 according to the obtained limit value range of the included angle between the outer joint axis and the shaft rod;
s3, establishing a mathematical model of the offset condition of the displacement of the inner joint bearing contact point, and correcting the value range of the length L of the driving shaft obtained in the step S2 according to the obtained limit value range of the displacement of the bearing contact point;
s4, selecting an optimal solution of the length L of the driving shaft according to the result of the step S3.
Further, step S1 includes the steps of:
as shown in fig. 1, a coordinate system is established, the abscissa is displacement, the ordinate is inner joint angle, the known points 1, 2, 3, 4 and 5 provided by a provider are sequentially connected into a straight line to form a limit value mathematical model, and the straight line equations of straight lines L1, L2 and L3 are obtained through the coordinates of the known points; the straight lines L1, L2 and L3 are obtained according to design experience;
the limit boundary is a set of (t, θ) coordinates capable of meeting technical requirements, and is generally provided for suppliers; the straight lines L1, L2 and L3 form a safety boundary, and the safety boundary is generally obtained by shifting a limit boundary by a certain safety amount, and the point coordinates (t, theta) of the inner joint of the driving shaft in the sliding process of each working condition are all in the safety boundary.
Further, as shown in fig. 3, let the theoretical inner node of the left driving shaft be O1, the actual inner node of the driving shaft be Ot, the outer node of the driving shaft be Mli, and any point on the outer node of the driving shaft (the end point of the outer node is taken in fig. 4) be Mlo;
setting the axial length of a driving shaft, namely the distance between Mli and Ot, as L, taking a Mli MliH vertical O1Ot extension line as a point H, setting +.MliOtH=θ, and setting O1Ot=t, namely the inner joint rotation angle θ, wherein the displacement of an inner joint is t;
from the known spatial coordinate system where O1Ot is parallel to the y-axis and the coordinates of O1 (x 1, y1, z 1), mli (xi, yi, zi) and Mlo (xo, yo, zo), the spatial geometrical relationship is known that the coordinates of the H-point are (x 1, yi, z 1), and the parametric equations of t and θ are found:
let the straight line L equation be: θ=kt+b,
substituting the formula (1) and the formula (2) into the straight line L equation yields the following equation:
order the
Wherein f (L) represents a series of straight line groups, which are parallel to the model boundary straight line; l obtained by f (L) =0 is a boundary point.
Further, the step S1 further includes the following steps:
and f (L) is derived to obtain:
when k < 0 (corresponding to the linear equation L3), F' (L) < 0, and F (L) is a decreasing function; if the root of f (L) =0 is Lx3, substituting f (L) into coordinates (t, θ) corresponding to all points on the left side of the straight line L3, wherein f (L) < 0 is found, and the value range of L is L > Lx3;
when k > 0 (corresponding to the linear equations L1 and L2), since θ < 30 DEG, k > 0.1, L > 300 in engineering practice, results
That is, F' (L) is greater than 0, and F (L) is obtained as an increasing function; if k and b in the equations of the straight lines L1 and L2 are taken to be respectively substituted into the obtained roots of f (L) =0 to be Lxb and Lxb2, f (L) is substituted into the coordinates (t, θ) corresponding to all points on the right sides of the straight lines L1 and L2, and f (L) < 0 is found, and the value range of L is L < min (Lxb 1, lxb 2);
finally, L is obtained in a value range of Lx3 < L < min (Lxb, lxb 2)
Further, as shown in fig. 2, step S2 includes the following steps:
setting the swing angle of the outer joint of the driving shaft as phi, and meeting the requirement that phi is less than phi 0 The psi is 0 To permit the work swing angle, the coordinates of Ot are (x 1, y1-t, z 1) from step S1, and the vector angle ψ is found from the space vectors MliMlo and OtMli:
conversion according to formula (3) gives:
wherein |OtMli| in formula (3) is L; the range of L is obtained by using inequality (4).
The outer joint swing angle psi of the driving shaft is the clamping angle between the outer joint axis and the axis of the driving shaft lever, and is smaller than Xu Yonggong as the swing angle psi 0 Said Xu Yonggong being a roll angle ψ 0 The value of (2) is generally 50 DEGOr around 50 deg.. In FIG. 2, the abscissa indicates the wheel heartbeat position corresponding to the outer joint of the driving shaft, and the ordinate indicates the swing angle value ψ of the corresponding working condition i All psi i Should be at psi 0 Below the line.
Further, step S3 includes the steps of:
angular conversion displacement t θ =tan (θ) ×λ/2, λ being a coefficient of conversion determined by the structure of the inner joint of the drive shaft;
the geometrical relationship of the inner joint structure of the driving shaft is as follows:
when the angular conversion displacement is greater than 0, the bearing contact point displacement t z ＝t+t θ ；
When the angular conversion displacement is smaller than 0, the bearing contact point displacement t z ＝t-t θ ；
If the design requires t z Should be at t m And t n Let t be z >t m And t is z <t n ；
According to the design requirement t z Selecting the value range of L meeting the requirement.
The bearing contact point displacement t z The displacement t converted from the inner joint displacement t and the inner joint rotation angle θ Calculated to obtain t z The values of (2) are in the range of-20 mm to +20mm, the specific requirements being given by the supplier.
And optimizing the driving shaft design by adopting MATLAB/GUI functions and an optimization function in an optimization tool box according to the system modeling, analysis and optimization objective function. The matrix data processing capability of MATLAB is very powerful, the GUI is one of MATALB to create a graphical user interface, the graphic user interface can be utilized to realize the visualization of the driving shaft design process through c language, and the graphic user interface has a good man-machine interaction function.
The invention establishes a driving shaft axial length fixed parameter optimization design program by utilizing the GUI function of MATLAB and an optimization tool box, and a main interface of the driving shaft axial length fixed parameter optimization design program is shown in figure 4. The position of the external node is determined along with the wheel jump, the coordinates of the external node are generated into excel at one time by three-dimensional software and then are imported into design software, the value range of the left and right driving shafts can be output, a user can select any solution in the value range, and the software calculates according to the solution and outputs the solution to a model corresponding to the excel to form a judging image.
And according to mathematical modeling of the optimization design of the axial length of the driving shaft, realizing a corresponding solving strategy through software.
Solving strategy of mathematical model of inner node displacement and inner node rotation angle:
coordinates of feature positions Mli (xi, yi, zi) and Mlo (xo, yo, zo) are generated in a suspension motion DMU model of the cata, the corresponding matrices of t and θ can be obtained by substituting the coordinate matrices into the formulas (1) and (2), the data in the matrices are substituted into three linear equations f (L) =0, the matrix of the solution of L can be obtained, and then the solution of L is [ Lx3] < L < min ([ Lxb ], [ lxb2 ]).
Solving strategy of mathematical model of outer joint rotation angle:
as is known from design experience, the allowable condition of the outer joint swing angle is easy to realize, so that the value range of L obtained by solving an equation is very large, and the significance of the final value instruction is not great, and a strategy of a test value method is adopted in calculation: and (3) taking integers from the calculated value range of L in the mathematical model of the inner node displacement and the inner node rotation angle to test values, and taking out the values meeting the inequality (4) to obtain the inequality solution meeting the requirements.
Solving strategy of mathematical model of inner joint bearing contact point displacement:
in the solving process of the mathematical model of the inner joint bearing contact point displacement, a test value method is also needed to solve, and the test value strategy is the same as that of the mathematical model of the outer joint rotation angle.
The test value process of the mathematical model of the outer joint rotation angle and the mathematical model of the inner joint bearing contact point displacement is easy to realize in computer calculation, so that the test value range can be properly enlarged, and the test value range is a solution of L in the mathematical model of the inner joint rotation angle and the inner joint rotation angle, and is a safe solution of the mathematical model meeting the limit value of the inner joint rotation angle and the inner joint rotation angle, and the condition without the solution can be possibly solved, and at the moment, the test value range can be replaced according to the engineering actual relaxation safe value.
The specific operation steps of the MATLAB software program are as follows:
step 1, filling input conditions required by the design of a driving shaft into an EXCEL template, wherein the content of the EXCEL template comprises:
a, theoretical internal node space coordinates of the driving shaft are defined as left side O1 and right side O2 as shown in table 1;
b, the coordinates of a steering gear rack stroke and a tire jumping stroke of each typical working condition in the suspension movement process and a corresponding left driving shaft outer joint node Mli and any point Mlo on an outer joint axis are in one-to-one correspondence with the coordinates of the outer joint related points of the table 2 and the table 3 as shown in the tables 2 and 3;
c, driving shaft inner joint sliding curve boundary points are shown in table 4, wherein An Quanliang is filled in according to design experience values;
d, drive shaft outer joint Xu Yonggong as a yaw angle limit, as shown in table 5;
e, coefficients of the drive shaft angle conversion displacement formula are shown in Table 6
TABLE 1
TABLE 2
| Exercise time | Steering (Rack travel) | Jumping (wheel jumping travel) |
| 20 | ||
| 30 | ||
| …… | ||
| 120 | ||
| 130 | ||
| …… | ||
| 230 | ||
| …… |
TABLE 3 Table 3
TABLE 4 Table 4
TABLE 5
TABLE 6
Wherein, table 1 is determined by the whole vehicle arrangement professional, table 2 and table 3 are input conditions of the chassis professional before cabin arrangement, and the information in table 4, table 5 and table 6 is determined by the attribute of the driving shaft, and is generally provided by a supplier.
s21, reading A, D, E information in the step 1, checking the information with a theoretical range, and if the information does not meet the requirements, suspending operation and reporting errors;
s22, reading A, B information in the step 1: the coordinates of the outer joint center and the points on the outer joint axis are in one-to-one correspondence with typical working conditions of suspension movement, the working conditions are coded into serial numbers in a template, and the serial numbers and the coordinates are correspondingly stored into a fixed array in the process of processing data by a program. During the storage process, the program will determine invalid data, and finally the array for calculation will reject the invalid data. And the space coordinates of the right driving shaft under each working condition are obtained by utilizing the characteristic that the space positions of the left and right outer sections of the driving shaft are symmetrical.
S23, defining an inner joint rotation angle a, an inner joint displacement t and a driving shaft axial length L, setting a vertical line to a straight line O1Ot through O1, setting a drop foot as H, setting an inner joint as Ot in the actual motion process of the driving shaft, and solving a parameter equation of a and t relative to L through a space triangle formed by space points Mli, O1, H, mli, ot and H.
S24, reading the information of the C in the step 1, and finding out the limit range of the inner joint slip curve, wherein the range consists of three straight lines, and the three straight line equations can be represented by a and t;
s25, combining the parameter equation in the step S23 and the linear equation set in the step S24 to form three equation sets about L, and finding a set of L values of L in a slip curve limit range through monotonicity judgment of a function about the L equation, wherein the set is defined as S.
S26, adding 20 to the maximum value of L in the set S, subtracting 20 from the minimum value to form a set Sa, obtaining an expression of the outer joint pivot angle about L by using a linear vector composed of Mli and Mlo and a linear vector composed of Ot and Mli, substituting the set S1 into the expression, obtaining a pivot angle set N corresponding to the set Sa, comparing the set N with the allowable pivot angle, and excluding L corresponding to all pivot angles which do not meet the requirement, wherein the rest of the set Sa is the L set meeting the pivot angle requirement of the driving shaft Xu Yonggong, and defining the set as S1.
S27, bearing contact point displacement z is translated into an expression of L, the relationship of z and L being provided by the drive shaft node supplier, typically the relationship shown in table 6. Substituting the data in Sa into the expression can calculate the swing angle set Z corresponding to the set Sa, compare the set Z with the allowable bearing contact point displacement, and exclude all L corresponding to the displacement which does not meet the requirement, so the rest of the set Z is the L set meeting the swing angle requirement of the driving shaft Xu Yonggong, and the set is defined as S2.
And S28, respectively outputting the sets S, S1 and S2, wherein the intersection of the sets is the set of the axial length of the driving shaft, and the set is a feasible scheme in design. The possibility of a right drive shaft can likewise be found by repeating the above steps. In the output process of S1 and S2, the computational analysis system will determine two sets: if S1 finally judges as an empty set, indicating that the L value which does not meet the outer joint swing angle requirement is not met, the system calculates corresponding working swing angle output as a reference by self-outputting a reference value, namely selecting a maximum value and a minimum value of an extension range of a set S (the minimum value in the set is extended by 8 units); if S2 is finally determined as an empty set, which indicates that the L value of the displacement requirement of the bearing contact point is not met, the system calculates the corresponding displacement output of the bearing contact point by taking the maximum value and the minimum value of the extension range of the set S (the minimum value in the set is extended by 8 units) as the reference value.
S29, respectively storing the Sa corresponding working condition number, the inner joint rotation angle, the outer joint rotation angle and the bearing contact point number groups, and defining the three groups as A, T, zt.
And 3, filling the inner joint rotation angle, the outer joint swing angle and the bearing contact displacement corresponding to the selected driving shaft length scheme into a template, observing the positions of corresponding characteristic curves in a checking model, and outputting a plurality of groups of images corresponding to L for comparison to find an optimal solution. The specific process is as follows:
s31, a reasonable L value is found through a set of sets S, S and S2, the value is input into a driving shaft design and analysis system, the system addresses the position of L in A, T, zt, the values of L corresponding to various working conditions in A, T, zt are sequentially output to corresponding positions in corresponding EXCEL templates, the process is completed by a writing algorithm of MATLAB to EXCEL, and finally, a characteristic curve is automatically displayed in the EXCEL;
s32, if the characteristic curve displayed above is not the optimal solution, L of a plurality of feasible schemes can be respectively input into the system, sheets in a plurality of EXCEL can be output after the system is processed, and the optimal solution is found through comparison of sheet images corresponding to the L, namely the final scheme of the driving shaft length.
Taking driving shaft parameters of an H7 four-wheel drive vehicle type as an example, specific data are as follows:
inner joint slip limiting model
(II) requirement of outer joint swing angle
| Xu Yonggong as a swing angle | 48 |
(III) angular conversion Displacement requirement
The template and the known condition data are imported into software, and the obtained data are obtained through solving as shown in fig. 5.
Based on the result shown in fig. 5, the middle value of the range of values of the left drive shaft length is selected to be 450mm, and the characteristic value is output as shown in fig. 6.
It can be seen from fig. 6 that the bearing contact point displacement is mostly positive, so that the lengthening of the drive shaft to 452mm is considered and the characteristic value is outputted as shown in fig. 7.
Then, according to the result shown in fig. 5, the middle value 361mm of the right driving shaft length value range is selected, and the characteristic value is output, as shown in fig. 8 (when the shaft length is 362mm according to the image offset rule, the image in the checking model is equivalent to 361 mm).
Finally, the parameters of the axial length of the left and right driving shafts of the four-wheel drive are selected to be 452mm and 361mm respectively according to the result.
The invention can complete the operation and check of 33 characteristic position working conditions required by the check standard at one time, and input characteristic data into the check template to form an image. The adopted software program can calculate the value range of the length of the driving shaft, and the driving shaft can be shared in a modular design in an intersection mode, so that the cost of the whole vehicle is reduced; and finishing the determination time of the left and right front driving shaft length parameters of a single vehicle type: the operation time of the designer is only 3 minutes, the background operation time of the system is about 7 minutes when the output file is formed, and compared with the traditional parameter setting process, the design efficiency is greatly improved.
The checking method establishes three mathematical models according to the space motion rule of the driving shaft: the inner node displacement and inner node corner mathematical model, outer node corner mathematical model and bearing contact displacement mathematical model, and according to the above mathematical model, the value range of the length of the driving shaft can be precisely calculated at one time through the coordinates of some points in the known three-dimensional data, compared with the traditional checking process, the working efficiency is obviously improved, and the method has more obvious advantages and significance in the whole vehicle modularized design process.
The foregoing has outlined rather broadly the preferred embodiments and principles of the present invention so that those skilled in the art may readily devise many other varied embodiments that, depending on the teaching presented herein, are still considered to be within the scope of the invention.
Claims (7)
1. The passenger car driving shaft arrangement checking method based on Matlab program is characterized by comprising the following steps of:
s1, establishing a mathematical model of limit values of inner node displacement and inner node rotation angle, and obtaining a value range of the length L of the driving shaft;
s2, establishing a mathematical model of the limit value of the outer joint rotation angle, and correcting the value range of the length L of the driving shaft obtained in the step S1 according to the obtained limit value range of the included angle between the outer joint axis and the shaft lever;
s3, establishing a mathematical model of the offset condition of the displacement of the inner joint bearing contact point, and correcting the value range of the length L of the driving shaft obtained in the step S2 according to the obtained limit value range of the displacement of the bearing contact point;
s4, selecting an optimal solution of the length L of the driving shaft according to the result of the step S3;
wherein, step S1 includes the following steps:
establishing a coordinate system, wherein the abscissa is displacement, the ordinate is inner joint angle, sequentially connecting the points 1, 2, 3, 4 and 5 provided by a provider into a straight line to form a limit mathematical model, and solving straight line equations of straight lines L1, L2 and L3 through the coordinates of the known points; the straight lines L1, L2 and L3 are obtained according to design experience;
setting the theoretical inner node of the driving shaft as O1, the actual inner node of the driving shaft as Ot, the outer node of the driving shaft as Mli and any point on the outer node of the driving shaft as Mlo;
setting the axial length of a driving shaft, namely the distance between Mli and Ot as L, taking a Mli MliH vertical O1Ot extension line as a point H, setting +.MliOtH=θ, and O1Ot=t, namely the inner joint rotation angle as θ, and the displacement of an inner joint as t;
from the known spatial coordinate system where O1Ot is parallel to the y-axis and the coordinates of O1 (x 1, y1, z 1), mli (xi, yi, zi) and Mlo (xo, yo, zo), the spatial geometrical relationship is known that the coordinates of the H-point are (x 1, yi, z 1), and the parametric equations of t and θ are found:
let the straight line L equation be:
，/>
substituting the formula (1) and the formula (2) into the straight line L equation yields the following equation:
order the
，
Wherein f (L) represents a series of straight line groups, which are parallel to the model boundary straight line; l obtained by f (L) =0 is a boundary point.
2. The passenger car drive shaft arrangement checking method based on Matlab program according to claim 1, wherein step S1 further comprises the steps of:
and f (L) is derived to obtain:
when k < 0, F' (L) < 0, F (L) is a decreasing function; if the root of f (L) =0 is Lx3, substituting f (L) into coordinates (t, θ) corresponding to all points on the left side of the straight line L3, wherein f (L) < 0 is found, and the value range of L is L > Lx3;
when k is more than 0, since θ is less than 30 DEG, k is more than 0.1, L is more than 300 in engineering practice, it is obtained
，
，/>
， />
I.e., F' (L) is greater than 0, to obtain F (L) as an increasing function; if k and b in the equations of the straight lines L1 and L2 are taken to be Lxb and Lxb, respectively, where f (L) =0, the coordinates (t, θ) corresponding to all points on the right side of the straight lines L1 and L2 are substituted for f (L), and f (L) is obtainedIf the value of L is less than 0, the value range of L is less than min (Lxb 1, lxb);
finally, the value range of L is Lx3 < L < min (Lxb, lxb 2).
3. The passenger car drive shaft arrangement checking method based on Matlab program according to claim 2, wherein step S2 includes the steps of:
the outer joint rotation angle of the driving shaft is set to be phi, thereby meeting the requirements of
Said->
To permit the work pivot angle, the coordinates of Ot are (x 1, y1-t, z 1) from step S1, and the vector angle ψ is found from the space vectors MliMlo and OtMli:
conversion according to formula (3) gives:
wherein |OtMli| in formula (3) is L; the range of L is obtained by using inequality (4).
4. A passenger car drive shaft arrangement checking method based on Matlab procedure according to claim 3, characterized in that step S3 comprises the steps of:
angular conversion displacement
Lambda is a conversion coefficient determined by the inner joint structure of the drive shaft;
the geometrical relationship of the inner joint structure of the driving shaft is as follows:
when the angular conversion displacement is greater than 0, the bearing contact point displacement
；
When the angular conversion displacement is less than 0, the bearing contact point displacement
；
If the design is required
Should be at->
And->
Between, let->
And->
；
According to design requirements
Selecting the value range of L meeting the requirement.
5. The method for checking the driving shaft arrangement of the passenger car based on the Matlab program according to claim 1, wherein the straight lines L1, L2 and L3 in the step S1 form a safety boundary, and the coordinates (t, θ) of points of the inner section of the driving shaft during the sliding process of each working condition are all within the safety boundary.
6. A method for checking a driving shaft arrangement of a passenger car based on a Matlab program according to claim 3, wherein the driving shaft outer joint swing angle ψ is an included angle between an outer joint axis and a driving shaft axis, and Xu Yonggong is a swing angle
The value of (2) is 50 deg..
7. The Matlab program-based passenger car drive shaft arrangement checking method according to claim 4, wherein the bearing contact point displacement
Displacement converted from inner joint displacement t and inner joint rotation angle +.>
Calculated out of->
The range of the value of (C) is-20 mm to +20mm.
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| US10358029B2 (en) * | 2015-11-02 | 2019-07-23 | Amanda Bent-Bolt Company | Floating differential suspension system |
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| CN210059397U (en) * | 2019-06-14 | 2020-02-14 | 钟祥市金祥汽车半轴有限公司 | Semi-axis correcting unit |
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