阅读说明：本技术 一种拖曳臂式四连杆悬架以及汽车 (Trailing arm type four-bar linkage suspension and automobile ) 是由 申文彬 韦文杰 梁毅 王芳 陈明 张德军 龙文 刘洋 李智健 程力 于 2021-03-31 设计创作，主要内容包括：本发明公开一种拖曳臂式四连杆悬架以及汽车,包括车身、副车架、上摆臂、弹簧摆臂、前束控制臂、转向节和拖曳臂；所述副车架前端与所述车身固定连接；所述转向节侧部可上下转动地安装有上摆臂、前束控制臂和弹簧摆臂,所述上摆臂远离所述转向节的一端和所述前束控制臂远离所述转向节的一端可上下转动地安装于所述副车架,所述弹簧摆臂远离所述转向节的一端可前后转动地连接于所述副车架；所述拖曳臂一端固定安装于所述转向节内侧,另一端可上下转动地安装于所述车身；其中,所述拖曳臂与所述车身的转动中心轴高于所述转向节中心点,以减小地面通过车轮传递到车身的冲击力,从而提升乘坐舒适性。(The invention discloses a trailing arm type four-connecting-rod suspension and an automobile, which comprise an automobile body, an auxiliary frame, an upper swing arm, a spring swing arm, a toe-in control arm, a steering knuckle and a trailing arm, wherein the upper swing arm is connected with the upper swing arm; the front end of the auxiliary frame is fixedly connected with the vehicle body; an upper swing arm, a toe-in control arm and a spring swing arm are mounted on the side portion of the steering knuckle in a vertically rotatable manner, one end of the upper swing arm, which is far away from the steering knuckle, and one end of the toe-in control arm, which is far away from the steering knuckle, are mounted on the auxiliary frame in a vertically rotatable manner, and one end of the spring swing arm, which is far away from the steering knuckle, is connected to the auxiliary frame in a vertically rotatable manner; one end of the towing arm is fixedly arranged on the inner side of the steering knuckle, and the other end of the towing arm is arranged on the vehicle body in a vertically rotatable manner; the rotation central shaft of the towing arm and the vehicle body is higher than the central point of the steering knuckle, so that the impact force transmitted to the vehicle body from the ground through wheels is reduced, and the riding comfort is improved.)

1. A trailing arm four-bar suspension comprising:

a vehicle body;

the front end of the auxiliary frame is fixedly connected with the vehicle body;

the side part of the steering knuckle is provided with an upper swing arm, a toe-in control arm and a spring swing arm in a vertically rotatable manner, one end of the upper swing arm, which is far away from the steering knuckle, and one end of the toe-in control arm, which is far away from the steering knuckle, are mounted on the auxiliary frame in a vertically rotatable manner, and one end of the spring swing arm, which is far away from the steering knuckle, is connected to the auxiliary frame in a vertically rotatable manner;

one end of the towing arm is fixedly arranged on the inner side of the steering knuckle, and the other end of the towing arm is arranged on the vehicle body in a vertically rotatable manner;

the rotation central shaft of the towing arm and the vehicle body is higher than the central point of the steering knuckle, so that the impact force transmitted to the vehicle body from the ground through the wheels is reduced.

2. The trailing arm type four-bar suspension according to claim 1, wherein a direction toward the rear in the longitudinal direction of the vehicle body is defined as an X direction, a direction toward the right in the width direction is defined as a Y direction, and a direction toward the upper side in the height direction is defined as a Z direction, a rectangular coordinate system is established with a point 100mm below a midpoint of a line connecting centers of two front wheels of the vehicle as an origin, and the X direction, the Y direction, and the Z direction are defined as axes;

the trailing arm type four-bar suspension is provided with a left rear wheel and a right rear wheel in bilateral symmetry, the right rear wheel is arranged on the steering knuckle, and the coordinates of the wheel center of the right rear wheel in the rectangular coordinate system are (x1, y1 and z1), wherein x1 is more than or equal to 2696mm, y1 is more than or equal to 268 mm and more than or equal to 268 mm, and z1 is more than or equal to 43mm and more than or equal to 53 mm;

the coordinates of the outer hard point of the spring swing arm in the rectangular coordinate system are (x2, y2, z2), wherein x2 is not less than 2751mm and not more than 2761mm, y2 is not less than 710mm and not more than 720mm, and z2 is not less than 63mm and not more than-53 mm;

the coordinates of the hard points in the spring swing arm in the rectangular coordinate system are (x3, y3, z3), wherein x3 is more than or equal to 2846mm and less than or equal to 2856mm, y3 is more than or equal to 133mm and less than or equal to 143mm, and z3 is more than or equal to 25mm and less than or equal to 35 mm;

the coordinates of the hard point outside the toe-in control arm in the rectangular coordinate system are (x4, y4, z4), wherein x4 is more than or equal to 2602mm and less than or equal to 2612mm, y4 is more than or equal to 711mm and less than or equal to 721mm, and z4 is more than or equal to 48mm and less than or equal to-38 mm;

the coordinates of the hard points in the toe-in control arm in the rectangular coordinate system are (x5, y5, z5), wherein x5 is more than or equal to 2598mm and less than or equal to 2608mm, y5 is more than or equal to 422mm and less than or equal to 432mm, and z5 is more than or equal to 23mm and less than or equal to 33 mm;

the coordinates of the hard point in the upper swing arm in the rectangular coordinate system are (x6, y6, z6), wherein x6 is not less than 2628mm and not more than 2638mm, y6 is not less than 402mm and not more than 412mm, and z6 is not less than 201mm and not more than 211 mm;

the coordinates of the upper swing arm outer hard point in the rectangular coordinate system are (x7, y7, z7), wherein x7 is more than or equal to 2636mm and less than or equal to 2646mm, y7 is more than or equal to 703mm and less than or equal to 713mm, and z7 is more than or equal to 147mm and less than or equal to 157 mm;

the coordinates of the hard point of the towing arm and the vehicle body in the rectangular coordinate system are (x8, y8, z8), wherein x8 is more than or equal to 2144mm and less than or equal to 2154mm, y8 is more than or equal to 621mm and less than or equal to 631mm, and z8 is more than or equal to 84mm and less than or equal to 94 mm.

3. The trailing arm four-bar suspension of claim 1, wherein the trailing arm and the knuckle are fixedly connected by a bolt fastener.

4. The trailing arm four-bar suspension of claim 1, wherein the trailing arm is pivotally connected to the vehicle body by a bushing, the bushing being a first rubber bushing.

5. The trailing arm four-bar suspension of claim 1 wherein the subframe is fixedly attached to the vehicle body by a second rubber bushing.

6. The trailing arm four-bar suspension of claim 1 wherein the upper swing arm is pivotally connected at each end to the subframe and the knuckle by a first bushing and a second bushing, respectively.

7. The trailing arm four-bar suspension of claim 1 wherein the swing spring arm is pivotally connected at each end to the subframe and the knuckle by a third bushing and a fourth bushing, respectively.

8. The trailing arm four-bar suspension of claim 1 wherein the toe control arm is pivotally connected at each end to the subframe and the knuckle by a fifth bushing and a sixth bushing, respectively.

9. The trailing arm four-link suspension of claim 2, wherein the right rear wheel hub has coordinates (x1, y1, z1) in the orthogonal coordinate system, wherein x1 ═ 2691mm, y1 ═ 793mm, z1 ═ 58 mm;

the coordinates of the spring swing arm outer hard point in the rectangular coordinate system are (x2, y2, z2), wherein x2 is 2756mm, y2 is 715mm, and z2 is-57 mm;

the coordinates of the hard point in the spring swing arm in the rectangular coordinate system are (x3, y3, z3), wherein x3 is 2851mm, y3 is 138mm, and z3 is 30 mm;

the coordinates of the toe-out control arm hard point in the rectangular coordinate system are (x4, y4, z4), wherein x4 is 2607mm, y4 is 716mm, and z4 is-43 mm;

the coordinates of the hard point in the toe-in control arm in the rectangular coordinate system are (x5, y5, z5), wherein x5 is 2603mm, y5 is 427mm, and z5 is 28 mm;

the coordinates of the hard point in the upper swing arm in the rectangular coordinate system are (x6, y6, z6), wherein x6 is 2633mm, y6 is 407mm, and z6 is 206 mm;

the coordinates of the upper swing arm outer hard point in the rectangular coordinate system are (x7, y7, z7), wherein x7 is 2641mm, y7 is 708mm, and z67152 mm;

the coordinate of the hard point of the towing arm connected with the vehicle body on the rectangular coordinate system is (x8, y8, z8), wherein x8 is 2149mm, y8 is 626mm, and z8 is 89 mm.

10. An automobile comprising the trailing arm type four-link suspension according to any one of claims 1 to 9.

Technical Field

The invention relates to the technical field of automobile suspensions, in particular to a trailing arm type four-bar linkage suspension and an automobile.

Background

The rear suspension of the existing mainstream vehicle type adopts a multi-link structure, the rear suspension is commonly provided with three links, a trailing arm type four link, an H arm four link and a five link, in order to obtain larger space for evacuation and taking a passenger, the transverse rod system of the multi-link is arranged compactly in the Z direction, the wheel center and the floor height are reduced as much as possible, and the wheel center yielding ratio is poorer and the comfort of the vehicle is influenced for the multi-link structure with the trailing arm type.

Disclosure of Invention

The invention mainly aims to provide a trailing arm type four-bar linkage suspension and an automobile, and aims to solve the problem of poor yielding of a wheel center of the automobile.

To achieve the above object, the present invention provides a trailing arm type four-bar suspension, comprising:

a vehicle body;

the front end of the auxiliary frame is fixedly connected with the vehicle body;

the side part of the steering knuckle is provided with an upper swing arm, a toe-in control arm and a spring swing arm in a vertically rotatable manner, one end of the upper swing arm, which is far away from the steering knuckle, and one end of the toe-in control arm, which is far away from the steering knuckle, are mounted on the auxiliary frame in a vertically rotatable manner, and one end of the spring swing arm, which is far away from the steering knuckle, is connected to the auxiliary frame in a vertically rotatable manner;

one end of the towing arm is fixedly arranged on the inner side of the steering knuckle, and the other end of the towing arm is arranged on the vehicle body in a vertically rotatable manner;

the rotation central shaft of the towing arm and the vehicle body is higher than the central point of the steering knuckle, so that the impact force transmitted to the vehicle body from the ground through the wheels is reduced.

Optionally, defining a backward direction of a vehicle body in a length direction as an X direction, a rightward direction of a width direction as a Y direction, and an upward direction of a height direction as a Z direction, and establishing a rectangular coordinate system by taking a point 100mm below a midpoint of a connecting line of centers of two front wheels of the vehicle as an origin, and taking the X direction, the Y direction, and the Z direction as axes;

the trailing arm type four-bar suspension is provided with a left rear wheel and a right rear wheel in bilateral symmetry, the right rear wheel is arranged on the steering knuckle, and the coordinates of the wheel center of the right rear wheel in the rectangular coordinate system are (x1, y1 and z1), wherein x1 is more than or equal to 2696mm, y1 is more than or equal to 268 mm and more than or equal to 268 mm, and z1 is more than or equal to 43mm and more than or equal to 53 mm;

the coordinates of the outer hard point of the spring swing arm in the rectangular coordinate system are (x2, y2, z2), wherein x2 is not less than 2751mm and not more than 2761mm, y2 is not less than 710mm and not more than 720mm, and z2 is not less than 63mm and not more than-53 mm;

the coordinates of the hard points in the spring swing arm in the rectangular coordinate system are (x3, y3, z3), wherein x3 is more than or equal to 2846mm and less than or equal to 2856mm, y3 is more than or equal to 133mm and less than or equal to 143mm, and z3 is more than or equal to 25mm and less than or equal to 35 mm;

the coordinates of the hard point outside the toe-in control arm in the rectangular coordinate system are (x4, y4, z4), wherein x4 is more than or equal to 2602mm and less than or equal to 2612mm, y4 is more than or equal to 711mm and less than or equal to 721mm, and z4 is more than or equal to 48mm and less than or equal to-38 mm;

the coordinates of the hard points in the toe-in control arm in the rectangular coordinate system are (x5, y5, z5), wherein x5 is more than or equal to 2598mm and less than or equal to 2608mm, y5 is more than or equal to 422mm and less than or equal to 432mm, and z5 is more than or equal to 23mm and less than or equal to 33 mm;

the coordinates of the hard point in the upper swing arm in the rectangular coordinate system are (x6, y6, z6), wherein x6 is not less than 2628mm and not more than 2638mm, y6 is not less than 402mm and not more than 412mm, and z6 is not less than 201mm and not more than 211 mm;

the coordinates of the upper swing arm outer hard point in the rectangular coordinate system are (x7, y7, z7), wherein x7 is more than or equal to 2636mm and less than or equal to 2646mm, y7 is more than or equal to 703mm and less than or equal to 713mm, and z7 is more than or equal to 147mm and less than or equal to 157 mm;

the coordinates of the hard point of the towing arm and the vehicle body in the rectangular coordinate system are (x8, y8, z8), wherein x8 is more than or equal to 2144mm and less than or equal to 2154mm, y8 is more than or equal to 621mm and less than or equal to 631mm, and z8 is more than or equal to 84mm and less than or equal to 94 mm.

Optionally, the trailing arm and the knuckle are fixedly connected by a bolt fastener.

Optionally, the trailing arm is rotatably connected with the vehicle body through a bushing, and the bushing is a first rubber bushing.

Optionally, the subframe is fixedly connected with the vehicle body through a second rubber bushing.

Optionally, two ends of the upper swing arm are correspondingly connected with the auxiliary frame and the steering knuckle in a rotating manner through a first bushing and a second bushing.

Optionally, two ends of the spring swing arm are correspondingly and rotatably connected with the auxiliary frame and the steering knuckle through a third bushing and a fourth bushing.

Optionally, both ends of the toe-in control arm are correspondingly and rotatably connected with the subframe and the steering knuckle through a fifth bushing and a sixth bushing.

Optionally, the coordinates of the right rear wheel center in the orthogonal coordinate system are (x1, y1, z1), where x1 is 2691mm, y1 is 793mm, and z1 is 58 mm;

the coordinates of the spring swing arm outer hard point in the rectangular coordinate system are (x2, y2, z2), wherein x2 is 2756mm, y2 is 715mm, and z2 is-57 mm;

the coordinates of the hard point in the spring swing arm in the rectangular coordinate system are (x3, y3, z3), wherein x3 is 2851mm, y3 is 138mm, and z3 is 30 mm;

the coordinates of the toe-out control arm hard point in the rectangular coordinate system are (x4, y4, z4), wherein x4 is 2607mm, y4 is 716mm, and z4 is-43 mm;

the coordinates of the hard point in the toe-in control arm in the rectangular coordinate system are (x5, y5, z5), wherein x5 is 2603mm, y5 is 427mm, and z5 is 28 mm;

the coordinates of the hard point in the upper swing arm in the rectangular coordinate system are (x6, y6, z6), wherein x6 is 2633mm, y6 is 407mm, and z6 is 206 mm;

the coordinates of the upper swing arm outer hard point in the rectangular coordinate system are (x7, y7, z7), wherein x7 is 2641mm, y7 is 708mm, and z67152 mm;

the coordinate of the hard point of the towing arm connected with the vehicle body on the rectangular coordinate system is (x8, y8, z8), wherein x8 is 2149mm, y8 is 626mm, and z8 is 89 mm.

The present invention also provides an automobile comprising:

a vehicle body;

the front end of the auxiliary frame is fixedly connected with the vehicle body;

the side part of the steering knuckle is provided with an upper swing arm, a toe-in control arm and a spring swing arm in a vertically rotatable manner, one end of the upper swing arm, which is far away from the steering knuckle, and one end of the toe-in control arm, which is far away from the steering knuckle, are mounted on the auxiliary frame in a vertically rotatable manner, and one end of the spring swing arm, which is far away from the steering knuckle, is connected to the auxiliary frame in a vertically rotatable manner;

one end of the towing arm is fixedly arranged on the inner side of the steering knuckle, and the other end of the towing arm is arranged on the vehicle body in a vertically rotatable manner;

the rotation central shaft of the towing arm and the vehicle body is higher than the central point of the steering knuckle, so that the impact force transmitted to the vehicle body from the ground through the wheels is reduced.

In the technical scheme of the invention, the center points of the towing arm and the connecting bush of the vehicle body are arranged above the wheel center of the rear wheel, when the center points of the towing arm and the connecting bush of the vehicle body are above the wheel center of the rear wheel, the included angle formed by the direction of the ground impact force applied to the rear wheel and the towing arm is larger than the included angle formed when the center points of the towing arm and the connecting bush of the vehicle body are below the wheel center of the rear wheel, the larger the included angle formed by the direction of the ground impact force and the towing arm is, the smaller the projection of the ground impact force on the towing arm is, when the magnitude of the ground impact force applied to the rear wheel is the same, the smaller the projection of the ground impact force on the towing arm is, correspondingly, the smaller the component force of the ground impact force on the towing arm is, so that the impact force transmitted to the vehicle body through the towing arm is smaller when, the wheel center yielding performance is improved, and the riding comfort is improved.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.

FIG. 1 is a schematic structural diagram of a trailing arm four-bar suspension according to an embodiment of the present invention;

FIG. 2 is a schematic diagram of a conventional suspension with a rear wheel being subjected to ground impact force;

fig. 3 is a schematic view of the rear wheel of the trailing arm type four-bar suspension according to the present invention receiving the impact force from the ground.

The reference numbers illustrate:

reference numerals	Name (R)	Reference numerals	Name (R)
				100	Trailing arm type four-bar suspension	41	Fifth bush
1	Trailing arm	42	Sixth bush
				11	First rubber bushing	5	Spring swing arm
12	Bolt fastener	51	Third bush
				2	Upper swing arm	52	Fourth bush
21	First bush	6	Auxiliary frame
				22	Second bushing	61	Second rubber bushing
3	Steering knuckle	7	Rear wheel
				4	Toe-in control arm

The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

It should be noted that, if directional indications (such as up, down, left, right, front, and back … …) are involved in the embodiment of the present invention, the directional indications are only used to explain the relative positional relationship between the components, the movement situation, and the like in a specific posture (as shown in the drawing), and if the specific posture is changed, the directional indications are changed accordingly.

In addition, if there is a description of "first", "second", etc. in an embodiment of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, the meaning of "and/or" appearing throughout includes three juxtapositions, exemplified by "A and/or B" including either A or B or both A and B. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.

The rear suspension of the existing mainstream vehicle type adopts a multi-link structure, the rear suspension is commonly provided with three links, a trailing arm type four link, an H arm four link and a five link, in order to obtain larger space for evacuation and taking a passenger, the transverse rod system of the multi-link is arranged compactly in the Z direction, the wheel center and the floor height are reduced as much as possible, and the wheel center yielding ratio is poorer and the comfort of the vehicle is influenced for the multi-link structure with the trailing arm type.

In view of this, the present invention provides a trailing arm type four-bar suspension, so that the central axis of rotation between the trailing arm and the vehicle body is higher than the center point of the knuckle, so as to reduce the impact force transmitted from the ground to the vehicle body through the wheels, thereby improving the riding comfort. FIG. 1 is a schematic diagram of an embodiment of the present invention.

In the present embodiment, as shown in fig. 1, the trailing arm type four-bar suspension 100 includes a vehicle body, a sub-frame 6, an upper swing arm 2, a spring swing arm 5, a toe control arm 4, a knuckle 3, and a trailing arm 1; the front end of the auxiliary frame 6 is fixedly connected with the vehicle body; an upper swing arm 2, a toe-in control arm 4 and a spring swing arm 5 are mounted on the side portion of the steering knuckle 3 in a vertically rotatable manner, one end of the upper swing arm 2, which is far away from the steering knuckle 3, and one end of the toe-in control arm 4, which is far away from the steering knuckle 3, are mounted on the auxiliary frame 6 in a vertically rotatable manner, and one end of the spring swing arm 5, which is far away from the steering knuckle 3, is connected to the auxiliary frame 6 in a vertically rotatable manner; one end of the towing arm 1 is fixedly arranged on the inner side of the steering knuckle 3, and the other end of the towing arm is arranged on the vehicle body in a vertically rotatable manner; the rotation central axis of the towing arm 1 and the vehicle body is higher than the central point of the steering knuckle 3, so that the impact force transmitted from the ground to the vehicle body through the wheels is reduced.

As shown in fig. 2, in the schematic diagram of the impact force applied to the ground by the rear wheel 7 of the conventional suspension, the rear wheel 7 is applied with the ground impact force F, an included angle between the impact force F and the trailing arm 1 is a, the trailing arm 1 is applied with the impact force F1 ═ F cosa, similarly, the first rubber bushing 11 is applied with the impact force F1, and the impact force applied to the vehicle body is F1;

as shown in fig. 3, the rear wheel 7 of the trailing arm type four-bar suspension provided by the present invention is subjected to a ground impact force, where the ground impact force applied to the rear wheel 7 is F ', an included angle between the impact force F' and the trailing arm 1 is a ', and the trailing arm 1 is subjected to an impact force F1' ═ F '× cosa', and similarly, the first rubber bushing 11 is subjected to an impact force F1', and the vehicle body is subjected to an impact force F1';

obviously, the included angle a ' > a, cosa ' > cosa, when the ground impact force applied to the rear wheel 7 is equal, that is, F ═ F ', F ' > cosa, then F1' > F1, therefore, the trailing arm type four-bar suspension provided by the present invention can effectively reduce the impact force applied to the vehicle body, and improve the wheel center yielding, thereby improving the riding comfort.

In this embodiment, as shown in fig. 1, a rearward direction of a vehicle body in a length direction is defined as an X direction, a rightward direction of a width direction is defined as a Y direction, and an upward direction of a height direction is defined as a Z direction, a point 100mm below a midpoint of a connecting line of centers of two front wheels of an automobile is taken as an origin, and a rectangular coordinate system is established by taking the X direction, the Y direction, and the Z direction as axes;

the trailing arm type four-bar suspension 100 is provided with a left rear wheel and a right rear wheel in bilateral symmetry, the right rear wheel is arranged on the steering knuckle 3, and the coordinates of the wheel center of the right rear wheel in the rectangular coordinate system are (x1, y1, z1), wherein x1 is more than or equal to 2696mm, y1 is more than or equal to 788mm and less than or equal to 798mm, and z1 is more than or equal to 43mm and less than or equal to 53 mm;

the coordinates of the outer hard point of the spring swing arm 5 in the rectangular coordinate system are (x2, y2, z2), wherein x2 is not less than 2751mm and not more than 2761mm, y2 is not less than 710mm and not more than 720mm, and z2 is not less than 63mm and not more than 53mm, and the outer hard point of the spring swing arm 5 is a kinematic characteristic point between the spring swing arm 5 and the steering knuckle 3, namely the centroid point of the fourth bushing 52;

the coordinates of the hard point in the spring swing arm 5 in the rectangular coordinate system are (x3, y3, z3), wherein x3 is more than or equal to 2846mm and less than or equal to 2856mm, y3 is more than or equal to 133mm and less than or equal to 143mm, z3 is more than or equal to 25mm and less than or equal to 35mm, and the hard point in the spring swing arm 5 is a kinematic characteristic point between the spring swing arm 5 and the subframe 6, namely a centroid point of the third bushing 51;

the coordinates of the hard point outside the toe control arm 4 in the rectangular coordinate system are (x4, y4, z4), wherein 2602mm is larger than or equal to x4 is smaller than or equal to 2612mm, 711mm is larger than or equal to y4 is smaller than or equal to 721mm, -48mm is larger than or equal to z4 is smaller than or equal to-38 mm, and the hard point inside the toe control arm 4 is the kinematic characteristic point between the toe control arm 4 and the knuckle 3, namely the centroid point of the sixth bushing 42;

the coordinates of the hard point in the toe-in control arm 4 in the rectangular coordinate system are (x5, y5, z5), wherein x5 is not less than 2598mm and not more than 2608mm, y5 is not less than 422mm and not more than 432mm, z5 is not less than 23mm and not more than 33mm, and the hard point in the toe-in control arm 4 is a kinematic characteristic point between the toe-in control arm 4 and the subframe 6, namely a centroid point of the fifth bushing 41;

the coordinates of the hard point in the upper swing arm 2 in the rectangular coordinate system are (x6, y6, z6), wherein x6 is not less than 2628mm and not more than 2638mm, y6 is not less than 402mm and not more than 412mm, z6 is not less than 201mm and not more than 211mm, and the hard point in the upper swing arm 2 is the kinematic characteristic point between the upper swing arm 2 and the subframe 6, namely the centroid point of the second bushing 22;

the coordinates of the outer hard point of the upper swing arm 2 in the rectangular coordinate system are (x7, y7, z7), wherein x7 is more than or equal to 2636mm and less than or equal to 2646mm, y7 is more than or equal to 703mm and less than or equal to 713mm, and z7 is more than or equal to 147mm and less than or equal to 157mm, and the inner hard point of the upper swing arm 2 is a kinematic characteristic point between the upper swing arm 2 and the knuckle 3, namely a centroid point of the first bushing 21;

the coordinates of the hard point of the towing arm 1 connected with the vehicle body in the rectangular coordinate system are (x8, y8, z8), wherein, x8 is more than or equal to 2144mm and less than or equal to 2154mm, y8 is more than or equal to 621mm and less than or equal to 631mm, and z8 is more than or equal to 84mm and less than or equal to 94mm, and the hard point of the bushing is the kinematic characteristic point between the towing arm 1 and the vehicle body, namely the centroid point of the first rubber bushing 11.

By controlling the coordinates of all the hard points in the rectangular coordinate system within the coordinate value range, the motion of the trailing arm type four-bar suspension 100 can be better controlled, so that the impact force of ground obstacles on the vehicle body can be reduced in a most reasonable manner, and better riding comfort is provided for the rear row.

In the present embodiment, as shown in fig. 1, the trailing arm 1 and the knuckle 3 are fixedly connected by a bolt fastener 12; the rear wheel can support the vehicle body, and meanwhile, a certain movement space is formed between the rear wheel and the vehicle body, so that a vibration damping space is provided.

In the present embodiment, as shown in fig. 1, the trailing arm 1 is rotatably connected to the vehicle body through a bushing, which is a first rubber bushing 11; there is not relative slip between rubber bush and the round pin, only rubber bush's elastic deformation, therefore there is not friction and wearing and tearing, also need not lubricate, has reduced the maintenance work, and there is not the noise when rubber bush takes place elastic deformation, and can subduct the vibration, can play the better damping effect than the metal lining, provides better travelling comfort for the passenger.

In this embodiment, as shown in fig. 1, the subframe 6 is fixedly connected to the vehicle body through a second rubber bushing 61, and the second rubber bushing 61 is made of rubber, so that the damping effect is good, the impact force on the vehicle body is reduced, and the riding comfort is improved.

In the present embodiment, as shown in fig. 1, both ends of the upper swing arm 2 are rotatably connected to the subframe 6 and the knuckle 3 through a first bushing 21 and a second bushing 22; the rotating capacity between each part can be greatly improved through the rotating connection of the lining, the service life of each part is prolonged, and the cost is saved.

In the present embodiment, as shown in fig. 1, both ends of the swing spring arm 5 are rotatably connected to the subframe 6 and the knuckle 3 through a third bushing 51 and a fourth bushing 52; the spring swing arm 5 has excellent elasticity, and when the rear wheel received the impact, trailing arm formula four-bar linkage suspension 100 wound first rubber bush 11 rotated, the spring swing arm 5 atress is crooked, slows down the impact that the automobile body received through elastic deformation, promotes riding comfort.

In the present embodiment, as shown in fig. 1, both ends of the toe control arm 4 are rotatably connected to the sub-frame 6 and the knuckle 3 via a fifth bushing 41 and a sixth bushing 42, respectively.

In the present embodiment, as shown in fig. 1, the coordinates of the right rear wheel center in the orthogonal coordinate system are (x1, y1, z1), where x1 equals 2691mm, y1 equals 793mm, and z1 equals 58 mm;

the coordinates of the outer hard point of the spring swing arm 5 in the rectangular coordinate system are (x2, y2, z2), wherein x2 is 2756mm, y2 is 715mm, and z2 is-57 mm, and the outer hard point of the spring swing arm 5 is a kinematic characteristic point between the spring swing arm 5 and the knuckle 3, namely a centroid point of the fourth bushing 52;

the coordinates of the hard point in the spring swing arm 5 in the rectangular coordinate system are (x3, y3, z3), wherein x3 is 2851mm, y3 is 138mm, and z3 is 30mm, and the hard point in the spring swing arm 5 is the kinematic characteristic point between the spring swing arm 5 and the subframe 6, that is, the centroid point of the third bushing 51;

the coordinates of the hard spot outside the toe control arm 4 in the rectangular coordinate system are (x4, y4, z4), where x4 is 2607mm, y4 is 716mm, and z4 is-43 mm, and the hard spot inside the toe control arm 4 is the kinematic characteristic point between the toe control arm 4 and the knuckle 3, that is, the centroid point of the sixth bushing 42;

the coordinates of the hard point in the toe-in control arm 4 in the rectangular coordinate system are (x5, y5, z5), where x5 is 2603mm, y5 is 427mm, and z5 is 28mm, and the hard point in the toe-in control arm 4 is the kinematic characteristic point between the toe-in control arm 4 and the subframe 6, that is, the centroid point of the fifth bushing 41;

the coordinates of the hard point in the upper swing arm 2 in the rectangular coordinate system are (x6, y6, z6), where x6 is 2633mm, y6 is 407mm, and z6 is 206mm, and the hard point in the upper swing arm 2 is the kinematic characteristic point between the upper swing arm 2 and the subframe 6, that is, the centroid point of the second bushing 22;

the coordinates of the outer hard point of the upper swing arm 2 in the rectangular coordinate system are (x7, y7, z7), where x7 is 2641mm, y7 is 708mm, and z67152mm, and the inner hard point of the upper swing arm 2 is the kinematic characteristic point between the upper swing arm 2 and the knuckle 3, i.e., the centroid point of the first bushing 21;

the coordinates of the hard point of the trailing arm 1 connected with the vehicle body in the rectangular coordinate system are (x8, y8, z8), wherein x8 is 2149mm, y8 is 626mm, and z8 is 89mm, and the hard point of the bushing is the kinematic characteristic point between the trailing arm 1 and the vehicle body, namely the centroid point of the first rubber bushing 11;

above-mentioned hard point sets up to best setting scheme, the impact force that can furthest reduction automobile body received, furthest's promotion riding comfort.

The invention also provides an automobile which comprises an automobile body, an auxiliary frame 6, an upper swing arm 2, a spring swing arm 5, a toe-in control arm 4, a steering knuckle 3 and a towing arm 1; the front end of the auxiliary frame 6 is fixedly connected with the vehicle body; an upper swing arm 2, a toe-in control arm 4 and a spring swing arm 5 are mounted on the side portion of the steering knuckle 3 in a vertically rotatable manner, one end of the upper swing arm 2, which is far away from the steering knuckle 3, and one end of the toe-in control arm 4, which is far away from the steering knuckle 3, are mounted on the auxiliary frame 6 in a vertically rotatable manner, and one end of the spring swing arm 5, which is far away from the steering knuckle 3, is connected to the auxiliary frame 6 in a vertically rotatable manner; one end of the towing arm 1 is fixedly arranged on the inner side of the steering knuckle 3, and the other end of the towing arm is arranged on the vehicle body in a vertically rotatable manner; the rotation central axis of the towing arm 1 and the vehicle body is higher than the central point of the steering knuckle 3, so that the impact force transmitted from the ground to the vehicle body through the wheels is reduced.

The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention, and all modifications and equivalents of the present invention, which are made by the contents of the present specification and the accompanying drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.