JPS61285110A - Suspension device for car - Google Patents

Abstract

PURPOSE:To increase a roll mode in a suspension device supporting a wheel supporting member swayably up and down via upper links and lower links arranged in the right and left direction of a car by making the car body side connecting point of the lower links movable and decreasing the in-lift during a turn. CONSTITUTION:A suspension device 10 for car supports spindles 13, 13a as a car supporting member swayably up and down to a car body 11 via upper links 14, 14a and lower links 15, 15a facing each other in the vertical direction of a car. In this case, an assist bar 20 directing in the right and left direction of the car is arranged below the center section of the car body 11, and the center section of this bar 20 is rotatably supported by the car body 11 via a pin 21. Sub-springs 22, 22a are inserted between both end sections of this assist bar 20 and the car body 11. Car inner end sections of the lower links 15, 15a are rotatably fitted to both end sections of the assist bar 20 via rubber bushes 23, 23a.

Description

[Detailed description of the invention] Industrial applications The present invention relates to a suspension system for a vehicle.

2. Description of the Related Art In general, there are many types of suspension systems for vehicles, and among them, a double wishbone type as shown in Japanese Utility Model Application No. 58-70911 is often used.

This double wishbone type suspension system 1 is the fifth
As shown in the figure, the spindles 3, 3a as wheel support members supporting the wheels 2.2a are connected to the upper link 4.4.
a and lower links 5, 5a to be vertically swingably connected to the vehicle body 6 side. In addition, a spring and a shock absorber (not shown) are installed between the lower link 5.5a and the vehicle body 6.The white circle in the figure indicates a rubber button, and this rubber button is the pivot point. .

Problems to be Solved by the Invention By the way, the conventional double wishbone type suspension system 1 has the possibility of being made superior in performance to other suspension systems due to its large degree of geometrical freedom. However, the problem is that the roll center normally moves toward the outer wheel during roll, which promotes in-lift when turning. In other words, the roll center 〇 of the double Witschbo/type connects the intersection point 01*ox of the extended line of the upper link 4.4a and the lower link 5, 5a and the grounding point of the wheels 2, 2a, as shown in the same figure. It is known that it is determined by the intersection of line segments tl and t. Therefore, when the vehicle body 6 is in a horizontal state as shown in FIG. 5, the roll center 0 is set on the vehicle center line P, but when the vehicle body 6 is turning, as shown in FIG. When rolled, the roll center P
is shifted to the outer wheel 2 side from the original vehicle center line. The reason why the roll center 〇 is shifted to the outer ring 2 side during turning in this way is that the upper links 4 and 4a have a finite length, and there is a problem in the structure of each link.

Therefore, the present invention changes the amount of inclination of the lower link during roll by making the connection point of the lower link movable on the vehicle body side, thereby shifting the roll center during turning to at least the inner wheel side from the vehicle center line. The purpose of the present invention is to provide a suspension system for a vehicle.

Means for Solving the Problems In order to achieve the above object, the present invention includes a pair of upper links and a lower link that face each other in the vertical direction of the vehicle and are respectively disposed in the left and right direction of the vehicle. In a vehicle suspension system in which a wheel support member is vertically swingably connected to the vehicle body via an upper link and a lower link, and a spring is distributed between the lower link and the vehicle body, the intermediate portion rotates toward the vehicle body. As well as being able to be installed,
An assist par is provided which is supported in the rotational direction via an elastic member, and the vehicle body side connection points of the lower link are rotatably attached to both ends of the assist par.

With the structure described above, the vehicle suspension system of the present invention has the following effects:
If the vehicle body rolls, and one side of the vehicle in the left and right direction of the vehicle is lowered and the thicker and thinner side of the vehicle is raised, the lower link on the rolled side will be
The load due to the lowering of the vehicle body is transmitted via the spring, and the load is reduced to the lower link on the opposite side due to the rise of the vehicle body. Then, the difference in the loads acting on the respective lower links acts on both ends of the assist bar, creating a couple, and the assist bar is rotated against the biasing force of the elastic member. For this reason, the amount of inclination of the left and right lower links is increased, respectively.

The intersection of the extension lines of the lower link approaches the inner ring side, so
The intersection of the line segments connecting these respective intersections and the grounding points of the left and right wheels, that is, the roll center, approaches the inner wheel side.

Example Hereinafter, embodiments of the present invention will be described in detail based on the drawings.

That is, FIG. 1 shows a schematic view of a vehicle suspension system 10 showing one embodiment of the present invention, where 11 is a vehicle body and 12.12a is a wheel. The wheel 12.12a is rotatably supported on a spindle 13.13a as a wheel support. 1
4.14a is an upper link, 15.15a is a lower link, and these upper links 14.14a.

The lower link 15.15a is arranged to face the left and right direction of the vehicle, and faces downward from the vehicle. The vehicle outer end of the upper link 14.14a is rotatably attached to the upper end of the spindle 13.13a via a rubber bush 16.16a, which is schematically indicated by a white circle in the figure (the same applies hereafter), and The vehicle outer end of the lower link 15.15a is likewise rotatably attached to the lower end of the spindle 13.13a via a rubber bush 17.17a. Further, the vehicle inner end of the upper link 14.14a is attached to the vehicle body 11 with a rubber bushing 18.18.
It is rotatably added via a. 20 is car body 1
The assist bar is located below the center of 1 and is oriented toward the left and right direction of the vehicle.
It is rotatably supported by the vehicle body 11 via 1.

Furthermore, a sub-spring 22.22a as an elastic member is disposed between both ends of the assist par 20 and the vehicle body 11, and the sub-spring 22.22a biases the assist par 200 in the rotating direction. It has become. The vehicle inner end of the lower link 15.15a is attached to both ends of the assist par 20 with rubber bushings 2.
It is rotatably mounted via 3.23a.

24.24a is the lower link 15.15a and the vehicle body 11
This spring 24 is compressed between
In addition to absorbing the vibrations of the wheels 12 and 12a received from the road surface by the wheels 12 and 12a, a shock absorber (not shown) is provided between the lower link lfi, 15a and the vehicle body 11, and this shock absorber Vibration damping is provided.

With the above configuration, the vehicle suspension fIIt10 of this embodiment
In this case, when the vehicle body 11 is in a horizontal state as shown in FIG. 2, the roll center 〇 is located on the vehicle center line P as in the conventional case. That is, when the vehicle body 11 is in a horizontal state in FIG.
The load (P) acting on the lower link 15.degree. 15a through the lower link (see figure) is equal on the left and right sides.

At this time, if the attachment point of the spring 24.24a on the lower link 15.15a side is set at the center of this link 15.15a, then half of the load (P) is applied to each end of the assist par 2 (). , 9 P/2 acts, and the assist par 20 is brought into a balanced state and the horizontal direction is maintained. Therefore, the heights of the rubber bushes 23.23a at the vehicle inner ends of the lower links 15.15a are the same on the left and right sides, and the upper links 14.14a and the lower links 1
5. Intersection of extension line of 15a 01 * 01 and wheel 12.
This means that the intersection point of the line segment Zl s tl connecting the grounding point of the vehicle 12a and the roll center 〇 is located on the vehicle center line P.

Next, we will discuss a case where the vehicle body 11 rolls during a turn (taking as an example a case where the vehicle body 11 tilts to the left in the figure).
Then, the vehicle body 11 is lowered and 2I! The spring 24 at i (left side in the figure) is shortened, and the load acting on one lower link 15 increases by P, and becomes P+ΔP.

On the other hand, the spring 24a on the side where the vehicle body 11 is raised (the right side in the figure) is stretched, and the load acting on the other lower link 15& is reduced from P to P-ΔP.

The assist parr 20 is rotated in the direction of the vehicle body 110 (counterclockwise), as shown in FIG. 3, against the biasing force of the sub-spring 22.22a. Then, the amount of inclination of the lower link 15.15a increases more than in the case where the vehicle inner end of the lower link 15.15a is directly connected to the vehicle body 11 as in the conventional case, and the amount of inclination of the upper link 14.14 increases.
Intersection o1.a of the extension line of lower link 15.15a. o,
each approach the inner ring 12a side. Therefore, these intersections o
The intersection between te 01 and the grounding point of the wheel 12.12a, the roll center 〇, is necessarily the inner ring 12a.
By moving closer to the side, the in-lift when turning is reduced and the roll mode is improved.

Similarly, in this embodiment, when the lower link 15.15a swings, as shown by the two-dot chain line in FIG. 4, when the vehicle body 11 is fixed, the intersection points A and B (nodes) of the swing appear. At this time, by changing the spring constants of the elastic members that support the assist parr 20, that is, the sub-springs 22, 22a, the amount of rotation of the assist parr 200 is changed, thereby moving the intersection points A and B in the left-right direction of the vehicle. Therefore, the intersection A like this.

By moving B, the apparent lower link 15.
15a length is changed. Therefore, the set position of the roll center C can be tuned by adjusting the spring constants of the sub-springs 22, 22a and the rigidities of the elastic members t and b.

In this embodiment, a sub-spring 22 is used as the elastic member.
22a is shown, but it goes without saying that the present invention is not limited to this, and that an elastic body such as rubber can also perform the same function.

As described in detail, the vehicle suspension system of the present invention includes:
An assist par is provided which is rotatably attached to the vehicle body side and is supported in the rotational direction via an elastic member, and the vehicle inner end of the lower link is attached to both ends of the assist par. When the vehicle body rolls, the assist par is rotated by the load acting on the lower link against the biasing force of the elastic member, so that the amount of inclination of the lower link is further increased. Therefore, since the intersection points of the extension lines of the upper link and the lower link approach the inner wheels when turning, it is possible to reduce the in-lift during turning and improve the roll mode, thereby improving maneuverability. Further, in the present invention, by adjusting the rigidity of the elastic member that supports the assist bar, the assist bar rotation cover is changed when the vehicle body rolls, and the intersection point when the lower link swings is moved. Therefore, the apparent length of the lower link is changed by the movement of the intersection in this way, and this provides an excellent effect in that the position setting of the roll center can be tuned.

[Brief explanation of the drawing]

FIG. 1 is a schematic configuration diagram of a vehicle suspension system according to an embodiment of the present invention, FIGS. 2 and 3 are explanatory diagrams showing the operating states of the vehicle suspension system of the present invention, and FIG. 4 is a diagram of the present invention. FIG. 5 is an explanatory view showing the operating state of the lower link and the assist bar in the vehicle suspension system of the invention. FIG. 6 is an explanatory diagram showing the operating states of conventional vehicle suspension systems. 10--Fist vehicle suspension system, 11--Vehicle body, 12.1
2a@@@wheel, 13.13aψ・ψ spindle (wheel support member), 14.14 a”・upper link,
15.15 a ”...Lower link, 20... Assist bar, 22.22 a...-Sub spring (elastic member).

Claims (1)

[Claims] (1) Equipped with a pair of upper links and lower links that face each other in the vertical direction of the vehicle and are respectively arranged in the left and right direction of the vehicle, and the wheel support member can swing vertically toward the vehicle body via these upper links and lower links. In a vehicle suspension system in which a spring is arranged between the lower link and the vehicle body, the intermediate portion is rotatably mounted on the vehicle body side and supported in the rotation direction via an elastic member. A suspension system for a vehicle, characterized in that an assist bar is provided, and connection points on the vehicle body side of the lower link are rotatably attached to both ends of the assist bar.