CN109388834B - Analysis method for kingpin inclination deviation of Macpherson suspension - Google Patents
Analysis method for kingpin inclination deviation of Macpherson suspension Download PDFInfo
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Abstract
The invention discloses an analysis method for the inclination angle deviation of a kingpin of a Macpherson suspension. The method comprises the following steps: and constructing a first closed-loop size chain comprising a rocker arm component ring in a front suspension main plane, constructing a second closed-loop size chain comprising a rocker arm component ring, a main pin component ring and three component rings respectively parallel to three coordinate axes of a whole vehicle coordinate system, performing independent variable, dependent variable and invariant setting, eliminating the rotation angle deviation of the intermediate variable rocker arm by using a direct linear method of size chain deviation analysis, obtaining the main pin inclination angle deviation represented by the independent variable deviation, and performing key control by taking the independent variable deviation of the first closed-loop size chain with great influence on the main pin inclination angle deviation as a functional size. According to the invention, the three-dimensional deviation is analyzed by a two-dimensional method, so that the calculation method is simplified, and the time of early theoretical analysis is saved; each component ring in the closed-loop size chain can be equivalent to a vector, so that each angle in the size chain has practical significance and is convenient for practical control.
Description
Technical Field
The invention relates to the field of automobile chassis assembly deviation analysis, in particular to a method for analyzing the inclination deviation of a main pin of a Macpherson suspension.
Background
With the development of the automotive industry in China, more and more enterprises and technicians are beginning to pay attention to the steering stability of automobiles. In an automobile chassis system, four-wheel positioning parameters such as a kingpin inner inclination angle, a kingpin back inclination angle, a wheel camber angle, a wheel toe angle and the like have the most obvious influence on the automobile operation stability. The reasonable four-wheel positioning parameters can enable the automobile to steer lightly, have certain steering return characteristics and can reduce the abrasion of tires. Currently, the attitude of the caster angle is controlled mainly through the design phase. However, during the production process, there is inevitably a manufacturing deviation of the parts, resulting in a difference between the kingpin inclination and the theoretical value.
MacPherson (MacPherson) suspension is a form of independent suspension that is currently common and is commonly used on the front wheels of vehicles. Briefly, macpherson suspension is mainly composed of springs, shock absorbers, rocker arms, and the like. In the prior art, the king pin inclination angle deviation of the Macpherson suspension is generally analyzed by establishing a three-dimensional size chain, so that the calculation is complex, the two-dimensional projection angle of the established three-dimensional size chain under the whole vehicle coordinate system has no practical physical meaning, and the actual control is inconvenient.
Disclosure of Invention
In order to solve the problems in the prior art, the invention provides an analysis method for the inclination angle deviation of a kingpin of a Macpherson suspension.
In order to achieve the above purpose, the invention adopts the following technical scheme:
a method for analyzing the inclination deviation of a main pin of a Macpherson suspension comprises the following steps:
the method comprises the steps that the center of a geometric figure formed by intersecting a front suspension part and a front suspension main plane is taken as a size chain node, the intersection point of the axis of a mounting transverse hole of a rocker arm and an auxiliary frame and the front suspension main plane is taken as a size chain node, a first closed-loop size chain is constructed in the front suspension main plane, one of the component rings is a rocker arm component ring, and the front suspension main plane is a plane formed by stretching the axis of a wheel and the axis of a shock absorber;
taking the length of each component ring of the first closed-loop size chain and the rotation angle of each component ring relative to the previous component ring as variables, performing independent variable, dependent variable and invariant setting, setting the rotation angle of the rocker arm component ring relative to the previous component ring, namely the rocker arm rotation angle, as the dependent variable, and obtaining an expression of the rocker arm rotation angle deviation along with the independent variable deviation change by using a direct linear method of size chain deviation analysis;
constructing a second closed-loop size chain formed by sequentially connecting component rings L1, L2, L3, L4 and L5, wherein L2 is a rocker arm component ring, L3 is a master pin component ring, L1, L4 and L5 are respectively parallel to three coordinate axes x, y and z of a whole vehicle coordinate system, and a mounting point on a front suspension of a size chain node and a central point of a front rocker arm transverse mounting hole of the size chain node are connected through L4, L5 and L1 which are connected end to end;
setting the lengths of L1, L2, L4 and L5 and the rotation angle of L2 relative to the previous component ring, namely the rotation angle of a rocker arm, as independent variables, setting the length of L3 and the rotation angle of the L3 relative to the previous component ring, namely the king pin inclination angle, as independent variables, setting the rotation angles of L1, L4 and L5 relative to the respective previous component ring as independent variables, and obtaining an expression of the king pin inclination angle deviation along with the variation of the independent variable deviation by using a direct linear method of dimensional chain deviation analysis;
and decomposing the rocker angle deviation of the first closed-loop size chain into three coordinate axes x, y and z of a whole vehicle coordinate system, replacing the rocker angle deviation of the second closed-loop size chain with the rocker angle deviation of the first closed-loop size chain to obtain a kingpin inclination angle deviation expression which does not contain the rocker angle deviation, and carrying out key control by taking the independent variable deviation with great influence on the kingpin inclination angle deviation as a functional size.
Further, the first closed-loop size chain includes the following 6 size chain nodes: the center of the spherical hinge is arranged on the front suspension and the rocker arm, the center point of a geometric figure formed by the intersection of the lower mounting bolt of the steering knuckle and the shock absorber and the front suspension main plane, the midpoint of the connecting line of the two mounting bolts of the shock absorber, the perpendicular feet which are arranged on the axis of the shock absorber through the midpoint of the two bolts, the mounting point of the shock absorber and the vehicle body, and the intersection of the axis of the rocker arm and the auxiliary frame mounting transverse hole and the front suspension main plane.
Compared with the prior art, the invention has the following beneficial effects:
according to the invention, the first closed-loop size chain comprising the rocker arm component ring is constructed in the front suspension main plane, the second closed-loop size chain comprising the rocker arm component ring, the main pin component ring and three component rings respectively parallel to three coordinate axes of the whole vehicle coordinate system is constructed, and the three-dimensional deviation is analyzed by a two-dimensional method, so that the calculation method is simplified, the complexity of deviation analysis is reduced, and the time of early theoretical analysis is saved; each component ring in the size chain can be equivalent to a vector, so that each angle in the size chain has practical significance and is convenient for practical control.
Drawings
FIG. 1 is a schematic diagram of a first closed-loop dimensional chain;
fig. 2 is a schematic diagram of a second closed-loop dimensional chain.
In FIG. 1, the center of the spherical hinge for mounting the ball joint on the front suspension and the rocker arm, the center point of the geometric figure formed by the intersection of the lower mounting bolt of the B-steering knuckle and the shock absorber with the front suspension main plane, the midpoint of the connecting line of the two mounting bolts of the C-shock absorber, the perpendicular line perpendicular to the shock absorber axis through the midpoint of the two bolts, the mounting point of the E-shock absorber and the vehicle body, and the intersection of the axis of the mounting transverse hole of the F-rocker arm and the auxiliary frame with the front suspension main plane.
Detailed Description
The invention is described in further detail below with reference to the accompanying drawings.
The embodiment of the invention discloses a method for analyzing the inclination angle deviation of a kingpin of a Macpherson suspension, which comprises the following steps:
101, taking the center of a geometric figure formed by intersecting a front suspension part and a front suspension main plane as a size chain node, taking the intersection point of the axis of a mounting transverse hole of a rocker arm and an auxiliary frame and the front suspension main plane as a size chain node, constructing a first closed-loop size chain in the front suspension main plane, wherein one component ring is a rocker arm component ring, and the front suspension main plane is a plane formed by stretching the axis of a wheel and the axis of a shock absorber;
in this step, the plane spanned by the wheel axis and the shock absorber axis is defined as the front suspension principal plane. Of course, the precondition for definition is that the wheel axis is coplanar with the shock absorber axis. Constructing a first closed-loop size chain in a defined front suspension main plane, wherein the construction method comprises the following steps of: for the front suspension part intersected with the front suspension main plane, taking the center of the geometric figure formed by intersection as a dimension chain node; for the front suspension parts which do not intersect the front suspension main plane, geometric processing is performed, for example, the center point of the mounting transverse hole of the rocker arm and the auxiliary frame is not located on the front suspension main plane, and the intersection point of the axis of the mounting transverse hole of the rocker arm and the auxiliary frame and the front suspension main plane is taken as a dimension chain node. And connecting the size chain nodes positioned on the front suspension main plane to obtain a first closed-loop size chain. Each component loop of the first closed-loop size chain may be equivalently a vector, the length and direction of which represent the size and direction of the physical quantity represented by the vector, respectively. Therefore, the angles in the first closed-loop dimensional chain have practical significance, and the actual control is facilitated. One component ring in the first closed-loop size chain is a rocker arm component ring, namely the length of the component ring is used for representing the size of the rocker arm, and the direction of the component ring is used for representing the direction of the rotating axis of the rocker arm. The rocker arm component rings are arranged in the first closed-loop dimensional chain to analyze the relationship between rocker arm angular deviation and manufacturing deviation of each front-overhang part.
102, taking the length of each component ring of a first closed-loop size chain and the rotation angle of each component ring relative to the previous component ring as variables, performing independent variable, dependent variable and invariant setting, setting the rotation angle of the rocker arm component ring relative to the previous component ring, namely the rocker arm rotation angle, as the dependent variable, and obtaining an expression of rocker arm rotation angle deviation represented by independent variable deviation by using a direct linear method of size chain deviation analysis;
the method comprises the steps of setting independent variables, dependent variables and invariant of a first closed-loop size chain, setting rocker arm rotation angles as dependent variables, and obtaining an expression of rocker arm rotation angle deviation represented by the independent variable deviation by using a direct linear method of size chain deviation analysis. The direct linear method in dimensional chain bias analysis is of relatively mature prior art and is not described in detail herein.
Step 103, constructing a second closed-loop size chain formed by sequentially connecting component rings L1, L2, L3, L4 and L5, wherein L2 is a rocker arm component ring, L3 is a master pin component ring, L1, L4 and L5 are respectively parallel to three coordinate axes x, y and z of a whole car coordinate system, and a front suspension mounting point of a size chain node and a central point of a front rocker arm transverse mounting hole of the size chain node are connected through L4, L5 and L1 which are connected end to end;
this step represents the kingpin with the connection between the upper and lower mounting points of the front overhang when constructing the second closed-loop dimensional chain. In addition to the rocker arm component ring L2 and the kingpin component ring L3, the second closed-loop dimensional chain also comprises component rings L1, L4, L5 parallel to the three coordinate axes x, y, z of the overall vehicle coordinate system, respectively. And after the L4, the L5 and the L1 are sequentially connected end to end, the center points of the front suspension upper mounting point and the rocker arm transverse mounting hole are connected, and the center points of the front suspension upper mounting point and the rocker arm transverse mounting hole are two size chain nodes of a second closed-loop size chain, as shown in fig. 2. The length change of L1, L4 and L5 can represent any relative position of two mounting hard points, and the length deviation of L1, L4 and L5 is equal to the sum of the position deviation of the two mounting hard points and the compression amount of rubber materials of the mounting parts.
The whole vehicle coordinate system in the step is a commonly used three-dimensional rectangular coordinate system, the origin of the coordinate system coincides with the mass center of the vehicle, when the vehicle is in a static state on a horizontal road surface, the x-axis is parallel to the ground, the front direction of the vehicle is the forward direction, the z-axis is the vertical direction, the upward direction is the forward direction, the y-axis is perpendicular to the x-axis and the z-axis, the left direction of the driver is the forward direction (the direction of the y-axis can also be obtained according to the right-hand rule according to the directions of the x-axis and the z-axis).
104, setting the length of L1, L2, L4 and L5 and the rotation angle of L2 relative to the previous component ring, namely the rotation angle of a rocker arm, as independent variables, setting the length of L3 and the rotation angle of the L3 relative to the previous component ring, namely the caster angle, as independent variables, setting the rotation angles of L1, L4 and L5 relative to the respective previous component ring as independent variables, and obtaining an expression of the caster angle deviation along with the variation of the independent variables by using a direct linear method of dimensional chain deviation analysis;
this step first sets the variable type of the second closed-loop size chain. Since the kingpin tilt deviation is the subject of the analysis of the present invention, the length of the kingpin component ring L3 and its rotation angle with respect to the previous component ring are set as dependent variables, and the rotation angle of L3 with respect to the previous component ring is the kingpin tilt. The rocker arm rotation angle deviation is an intermediate variable for analyzing the kingpin inclination angle deviation, so the rotation angle of the rocker arm component ring L2 with respect to the previous component ring is set as an independent variable. L1, L4, L5 are parallel to three coordinate axes of the whole vehicle coordinate system respectively, and the length change of the coordinate axes represents the position degree change of the mounting hard point, so the lengths of L1, L4 and L5 are set as independent variables, and the rotation angles of L1, L4 and L5 relative to the previous component rings are set as invariables. After the variable is set, an expression that the kingpin inclination angle deviation changes along with the independent variable deviation is obtained by using a direct linear method of size chain deviation analysis.
And 105, decomposing the rocker angle deviation of the first closed-loop size chain into three coordinate axes x, y and z of a whole vehicle coordinate system, replacing the rocker angle deviation of the second closed-loop size chain with the rocker angle deviation of the first closed-loop size chain to obtain a kingpin inclination angle deviation expression without the rocker angle deviation, and performing key control by taking the independent variable deviation with great influence on the kingpin inclination angle deviation as a functional size.
In the step, firstly, the rocker arm corner deviation of a first closed-loop size chain is decomposed into three coordinate axes x, y and z of a whole vehicle coordinate system (the decomposition method is to multiply the rocker arm corner deviation of the first closed-loop size chain by cosine of angles between the rotation axis of the rocker arm and the three coordinate axes respectively); the rocker arm angle deviation of the first closed-loop size chain is then substituted for the rocker arm angle deviation of the second closed-loop size chain. Because the rocker angle deviation of the first closed-loop size chain has been represented by the independent variable deviation of the first closed-loop size chain in step 102, the intermediate variable-rocker angle deviation in the kingpin angle deviation analysis expression is eliminated after the above substitution. And finally, finding out independent variable deviation with great influence on the kingpin inclination angle deviation according to the expression, and performing key control by taking the part manufacturing deviation represented by the independent variable deviation as a functional size. The expression obtained according to the direct linear method is a linear expression, and an independent variable having a large absolute value of a coefficient (also referred to as a sensitivity coefficient) in the expression has a large influence on a dependent variable.
As an alternative embodiment, the first closed-loop size chain comprises the following 6 size chain nodes: the center of the spherical hinge is arranged on the front suspension and the rocker arm, the center point of a geometric figure formed by intersecting a lower mounting bolt of the steering knuckle and the shock absorber with a front suspension main plane, the midpoint of a connecting line of the two mounting bolts of the shock absorber, the perpendicular feet which are arranged on the axis of the shock absorber through the midpoint of the two bolts, the mounting point of the shock absorber and the vehicle body, and the intersection point of the axis of a mounting transverse hole of the rocker arm and the auxiliary frame with the front suspension main plane.
The embodiment shows a specific first closed-loop size chain constructed in the front suspension main plane, wherein the 6 size chain nodes of the first closed-loop size chain are all located in the front suspension main plane, and as shown in fig. 1, the 6 size chain link points are respectively: a is the center of a spherical hinge for installing a front suspension and a rocker arm, B is the center point of a geometric figure formed by intersecting a lower installation bolt of a steering knuckle and a shock absorber with a front suspension main plane, C is the midpoint of a connecting line of two installation bolts of the shock absorber, D is the perpendicular line perpendicular to the shock absorber axis through the midpoint of the two bolts, E is the installation point of the shock absorber and a vehicle body, and F is the intersection point of the axis of an installation transverse hole of the rocker arm and an auxiliary frame and the front suspension main plane. Directed line segment AB, BC, CD, DE, EF and FA divisionThe 6 constituent rings L of the first closed-loop size chain 1 '、L 2 '、L 3 '、L 4 '、L 5 ' and L 6 '。
An example of application of the present invention is given below.
Construction of 6 component rings L in the front suspension principal plane 1 '、L 2 '、L 3 '、L 4 '、L 5 ' and L 6 The first closed-loop dimensional chain of 'composition, as shown in fig. 1, wherein L6' is the rocker arm composition ring. With L 1 '、L 2 '、L 3 '、L 4 '、L 5 '、L 6 'represents the length of 6 constituent rings, θ' 1 、θ′ 2 、θ′ 3 、θ′ 4 、θ′ 5 、θ′ 6 Indicating the rotation angle (counterclockwise) of each component ring with respect to the previous component ring. Will L 1 '、L 2 '、L 3 '、L 4 'and θ' 1 、θ′ 2 、θ′ 3 、θ′ 4 Set as an independent variable, L 5 'and θ' 5 、θ′ 6 Set as dependent variable, let L 6 ' set to invariant. According to a direct linear method of size chain deviation analysis, an expression that the rocker arm rotation angle deviation changes along with eight independent variable deviations is obtained:
Δθ′ 6 ＝-0.8854ΔL' 1 -0.6387ΔL' 2 -0.5909ΔL' 3 -0.6138ΔL' 4
+0.8518Δθ′ 1 +0.5287Δθ′ 2 -1.3564Δθ′ 3 +0.5268Δθ′ 4
wherein "Δ" represents a deviation, such as Δθ' 6 Is the rocker arm rotation angle deviation; the coefficients before each deviation are called the sensitivity coefficients.
A second closed-loop size chain consisting of 5 component rings L1, L2, L3, L4 and L5 is constructed, as shown in figure 2, wherein L2 is a rocker arm component ring, L3 is a master pin component ring, and L1, L4 and L5 are respectively parallel to three coordinate axes x, y and z of a whole vehicle coordinate system. By L 1 、L 2 、L 3 、L 4 、L 5 Respectively representing the lengths of 5 constituent rings, using θ 1 、θ 2 、θ 3 、θ 4 、θ 5 Each representing the rotation angle of 5 component rings relative to the previous component ring. Will L 1 、L 2 、L 4 、L 5 And theta 2 Set as independent variable, length L of main pin forming ring 3 And kingpin tilt angle theta 3 Setting as dependent variable, θ 1 、θ 4 、θ 5 Is set to be invariable. And obtaining an expression that the kingpin inclination angle deviation changes along with the respective variable deviation according to a direct linear method of the dimensional chain deviation analysis. And decomposing the rocker arm corner deviation obtained in the first closed-loop size chain into three coordinate axes x, y and z of a whole vehicle coordinate system, and replacing the rocker arm corner deviation of the second closed-loop size chain, so that the intermediate variable-rocker arm corner deviation in the king pin inclination angle deviation is eliminated, and the final relation between the king pin inclination angle deviation and the respective variable deviation is obtained, as shown in tables 1 and 2.
Table 1 king pin tilt angle offset expressed in terms of rocker arm angle offset
| ΔL 1 | ΔL 2 | ΔL 4 | ΔL 5 | Δθ 2x | Δθ 2y | Δθ 2z | |
| Δθ 3x | -0.455 | 0.002 | -0.003 | 0.0367 | -1.1588 | 0.0001 | 0.0128 |
| Δθ 3y | 0.0029 | -0.4630 | 0.4701 | 0.1056 | 0.0010 | -1.0103 | 0.0368 |
| Δθ 3z | 0.0085 | 0.0279 | -0.0280 | -0.0070 | 0.0030 | 0.0006 | -1.0025 |
TABLE 2 kingpin tilt bias after elimination of intermediate variable rocker arm corner bias
| ΔL 1 | ΔL 2 | ΔL 4 | ΔL 5 | ΔL' 1 | ΔL' 2 | ΔL' 3 | ΔL' 4 | Δθ 1 ' | Δθ 2 ' | Δθ 3 ' | Δθ 4 ' | |
| Δθ 3x | -0.450 | 0.002 | 0 | 0.037 | 1.025 | 0.739 | 0.684 | 0.710 | -0.99 | -0.61 | 1.570 | -0.610 |
| Δθ 3y | 0.003 | -0.460 | 0.470 | 0.106 | 0.007 | 0.005 | 0.005 | 0.005 | -0.010 | 0 | 0.011 | 0 |
| Δθ 3z | 0.009 | 0.028 | -0.030 | -0.010 | -0.130 | -0.100 | -0.090 | -0.090 | 0.129 | 0.080 | -0.200 | 0.080 |
The numbers in tables 1 and 2 are the sensitivity coefficients, deltaθ 3y Represents the inclination angle deviation of the kingpin, delta theta 3z Representing caster deviation. As can be seen from Table 2, Δθ' 3 For caster deviation delta theta of kingpin 3z Is large in the influence of the rocker arm length deviation DeltaL 2 For the inclination angle deviation delta theta of the kingpin 3y These two dimensions can be classified as important control functional dimensions, both of which lie in the principal plane of the front overhang.
The foregoing description of the embodiments of the present invention should not be taken as limiting the scope of the invention, but rather should be construed as falling within the scope of the invention, as long as the invention is modified or enlarged or reduced in terms of equivalent variations or modifications, equivalent proportions, or the like, which are included in the spirit of the invention.
Claims (1)
1. A method for analyzing a kingpin tilt angle deviation of a macpherson suspension, comprising:
the method comprises the steps that the center of a geometric figure formed by intersecting a front suspension part and a front suspension main plane is taken as a size chain node, the intersection point of the axis of a mounting transverse hole of a rocker arm and an auxiliary frame and the front suspension main plane is taken as a size chain node, a first closed-loop size chain is constructed in the front suspension main plane, one of the component rings is a rocker arm component ring, and the front suspension main plane is a plane formed by stretching the axis of a wheel and the axis of a shock absorber;
taking the length of each component ring of the first closed-loop size chain and the rotation angle of each component ring relative to the previous component ring as variables, performing independent variable, dependent variable and invariant setting, setting the rotation angle of the rocker arm component ring relative to the previous component ring, namely the rocker arm rotation angle, as the dependent variable, and obtaining an expression of the rocker arm rotation angle deviation along with the independent variable deviation change by using a direct linear method of size chain deviation analysis;
constructing a second closed-loop size chain formed by sequentially connecting component rings L1, L2, L3, L4 and L5, wherein L2 is a rocker arm component ring, L3 is a master pin component ring, L1, L4 and L5 are respectively parallel to three coordinate axes x, y and z of a whole vehicle coordinate system, and a mounting point on a front suspension of a size chain node and a central point of a front rocker arm transverse mounting hole of the size chain node are connected through L4, L5 and L1 which are connected end to end;
setting the lengths of L1, L2, L4 and L5 and the rotation angle of L2 relative to the previous component ring, namely the rotation angle of a rocker arm, as independent variables, setting the length of L3 and the rotation angle of the L3 relative to the previous component ring, namely the king pin inclination angle, as independent variables, setting the rotation angles of L1, L4 and L5 relative to the respective previous component ring as independent variables, and obtaining an expression of the king pin inclination angle deviation along with the variation of the independent variable deviation by using a direct linear method of dimensional chain deviation analysis;
decomposing the rocker angle deviation of the first closed-loop size chain into three coordinate axes x, y and z of a whole vehicle coordinate system, replacing the rocker angle deviation of the second closed-loop size chain with the rocker angle deviation of the first closed-loop size chain to obtain a kingpin inclination angle deviation expression which does not contain the rocker angle deviation, and carrying out key control on the independent variable deviation with great influence on the kingpin inclination angle deviation as a functional size;
the first closed-loop size chain includes the following 6 size chain nodes: the center of the spherical hinge is arranged on the front suspension and the rocker arm, the center point of a geometric figure formed by the intersection of the lower mounting bolt of the steering knuckle and the shock absorber and the front suspension main plane, the midpoint of the connecting line of the two mounting bolts of the shock absorber, the perpendicular feet which are arranged on the axis of the shock absorber through the midpoint of the two bolts, the mounting point of the shock absorber and the vehicle body, and the intersection of the axis of the rocker arm and the auxiliary frame mounting transverse hole and the front suspension main plane.
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5435591A (en) * | 1992-12-28 | 1995-07-25 | Hyundai Motor Co. | Steerable front wheel suspension for vehicle |
| CN102495927A (en) * | 2011-12-02 | 2012-06-13 | 北京理工大学 | Space dimension chain tolerance analytical method based on graphic representation |
| CN103310047A (en) * | 2013-05-30 | 2013-09-18 | 同济大学 | Optimization method facing lateral force of Macpherson suspension shock absorber |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US20080119978A1 (en) * | 2006-11-20 | 2008-05-22 | Hunter Engineering Company | Method and Apparatus For Wheel Assembly Force Moment Arm Measurement |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5435591A (en) * | 1992-12-28 | 1995-07-25 | Hyundai Motor Co. | Steerable front wheel suspension for vehicle |
| CN102495927A (en) * | 2011-12-02 | 2012-06-13 | 北京理工大学 | Space dimension chain tolerance analytical method based on graphic representation |
| CN103310047A (en) * | 2013-05-30 | 2013-09-18 | 同济大学 | Optimization method facing lateral force of Macpherson suspension shock absorber |
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