KR910006495Y1 - Suspension apparatus - Google Patents

Abstract

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Description

Rear wheel suspension of automobile

1 is a partially enlarged cross-sectional view of FIG.

2 is a II-II cross-sectional view of FIG.

3 is a plan view of an essential part of the rear wheel suspension of the vehicle according to the embodiment of the present invention.

* Explanation of symbols for main parts of the drawings

1: suspension frame 2: trailing arm

3: torsion beam 4: bodywork bracket

5: wheel 11: bushing housing (bush housing)

12 bush 13 spacer

15,16: Home

The present invention relates to a rear wheel suspension of an automobile, and more particularly, to a driving portion by the vehicle body side of the rear wheel suspension.

Conventionally H-shaped suspension consisting of a torsion beam connecting a pair of left and right trailing arms and a pair of trailing arms, as disclosed in Japanese Patent Application Laid-Open No. 58-90814, as a rear suspension. Torsion beam rear wheel suspension using frames is well known.

However, in such a torsion beam rear wheel suspension device, when the front end portion of the torsion beam is extracted so as to swing freely in the vertical direction with respect to the vehicle body, a bush having a moderate degree of elasticity is interposed therebetween.

However, since the spring characteristic is set as a normal bush has the same spring characteristics for the displacement on the front side and the displacement on the rear side of the vehicle body, the direction of the load applied to the connection between the trailing arm and the vehicle body. And when the size is changed according to the driving state of the car, there is no room for improvement, and there is room for improvement in terms of comfort and steering stability when riding.

The present invention aims to improve the problems pointed out in the related art as described above, in order to improve the comfort and steering stability when riding in a vehicle equipped with a trailing arm type rear wheel suspension.

The present invention smoothes the spring characteristics of the bush interposed between the trailing arm and the vehicle body as a means for achieving the above object in the direction in which the trailing arm is displaced in the rear of the vehicle body in the direction of displacement of the trailing arm toward the front of the vehicle body. It is set as possible.

In the present invention, as described above, when the wheel is caught in an obstacle such as a stone while the vehicle is under rapid acceleration or while driving, the connection part between the vehicle body and the trailing arm is similar to that of the vehicle body. In the state of impact loads such as displacing the trailing arms toward the rear of the vehicle, the soft spring characteristics of the bush have been described above, so that the shock loads are absorbed and relaxed, which improves the comfort when riding the car. As in the case of ring driving, the toe angle change of the wheel depends on the rigid spring characteristics of the bush when a load such as displacing the trailing arm toward the rear of the body is applied to the connection between the body and the trailing arm. It is suppressed as much as possible to improve the steering stability.

Next, the most suitable embodiment of the present invention will be described with reference to FIGS.

3 shows a rear wheel suspension device Z for a current driven vehicle according to an embodiment of the present invention.

This rear-wheel suspension Z is a so-called trailing arm type suspension device, which is a pair of right and left trailing arms 2 and 2 arranged at both sides of the vehicle body (not illustrated) and facing in the front and rear directions of the vehicle body. It has a substantially H-shaped suspension frame 1 of a torsion beam 3 connecting the middle portions of the arms 2 and 2 to each other.

The trailing arm 2 has a front end portion 2a located on its own front side (arrow F direction) so as to be freely swinged up and down with respect to the vehicle body via the bush 12 as described later. axis L _1, L ₁₎ to the device the other hand, the rear side of the vehicle body (after in the arrow R direction) end portion (2b), there is supported so that the wheel 5 is rotated freely.

As shown in FIGS. 1 and 2, the tip portion 2a of the trailing arm 2 is provided with a flange-like bush housing 11 facing the swing axis L ₁ in the direction following. have. In this bushing 11, an approximately fleshy cylindrical body 12a and an end of the movable body 12a having an external dimension that can be elastically pressed and inserted into the bushing 11 are provided. It is made by inserting the rubber bush 12 which consists of a disk-shaped flange 12b continuously formed. In addition, a metallic spacer 13 is integrally provided at the shaft center portion of the bush 12.

Furthermore, on the outer circumferential surface of the body 12a, the bush 12 further has a pair of grooves 15 and 16 at the positions opposite to each other with its central axis interposed in the radial direction, respectively. It is formed along the length.

Among the pair of grooves 15 and 16, one of the first grooves 15 has an arcuate groove bottom face 15a having a radius of curvature R ₁ , and an angle α in the circumferential direction (in this embodiment). a vertical groove having an opening width (groove width) of α = 60 °.

On the other hand, the second groove 16 on the other side has formed an arc-shaped groove bottom face 16a having a radius of curvature R ₂ larger than the radius of curvature R ₁ of the first groove 15 by a suitable size, and the first groove thereon. A vertical groove having an opening width angle β (which is set to be β = 90 ° in this embodiment) is larger than the opening width angle α of (15).

In the case of connecting the distal end portion 2a of the trailing arm 2 to the vehicle body side via a vehicle body bracket 4 for fastening to the vehicle shaft, the bushing 11 of the trailing arm 2 The bush 12 is inserted, and in this state, the left and right pairs of fixed plates 7 and 7 and the bush 12 are penetrated into the spacer 13 of the bush 12 in this state. It is made by connecting by the bearing (6) bearing.

(That is, the trailing arm 2 and the vehicle body bracket 4 are elastically connected to each other via the bush 12).

At this time, as shown in FIG. 2, the bush 12 has the first groove 15 at the front side of the vehicle body (i.e., at the tip side of the trailing arm 2, in the direction of arrow F in FIG. 2). Position 16 relative to the trailing arm 2 so as to face the vehicle body rear side (i.e., the rear end side of the trailing arm 2, arrow R in FIG. 2).

In this way, the size of the pair of grooves 15, 16 formed on the outer circumferential surface of the bush 12 is different from each other, and the bushing 11 is formed at a predetermined position, respectively. (12) refers to the case where the trailing arm 2 is relatively displaced to the front side of the vehicle body (referred to as forward displacement in the following description) and to the rear side of the vehicle body (rear displacement is explained in the following description). ) Has different spring characteristics. That is, when the trailing arm 2 is displaced forward, the inner peripheral surface 11a of the bushing 11 is slightly displaced in the direction of the arrow F of the bushing 11 so that the groove bottom 16a of the second groove 16 is located. In this case, the spring characteristics of the bush 12 are relatively hard in this case, and in the case of the rearward displacement, the bush until the displacement is considerably large in the direction of the arrow R of the bushing 11 is prevented. Since the inner circumferential surface 11a of the housing 11 and the groove bottom face 15a of the first groove 15 of the bush 12 do not contact each other, the spring characteristic of the bush 12 in this case is lower than that of the front displacement. It is soft.

In this embodiment, as shown in FIG. 3, the trailing arm 2 is formed on the curved arm to connect the bodywork bracket 4 and the trailing arm 2 to the center of the bearing bolt 6. As the shaft is inclined with respect to the torsion beam (3), the two swing axes L ₁ and L ₁ of the torsion beam (3) face each other toward the trailing arm (2) on the side of the swing support point in the horizontal plane. It is tilted.

When the vehicle is in a steady driving such as driving linearly at a constant speed, the magnitude of the load applied to the vehicle body and the trailing arm 2 and the connecting portion is relatively small, and the load direction thereof is also substantially constant. As shown in FIG. 2, the bush 12 elastically supports the vehicle body and the trailing arm 2 as it is in a state close to the normal state. Therefore, in this state, transmission of vibration from the wheel 5 side to the vehicle body side is reduced as much as possible, so that a good ride comfort can be obtained.

On the other hand, the vehicle may start rapidly when the vehicle is stopped or the rear wheel may not be moved by obstacles such as stones in the normal driving state, as shown in the direction of arrow F _A in FIG. 3 on the wheel 5. When a shock load such as the wheel 5 is pulled back toward the rear of the vehicle body is applied, the load Fa in the direction of displacing the trailing arm 2 (ie, bushing housing 11) is applied to the bush 12 portion. Works. However, in this embodiment, as described above, since the spring characteristic of the bush 12 is set so as to be soft with respect to the rearward displacement, the shock load Fa described above is absorbed by the bush 12 as much as possible and almost transmitted to the vehicle body side. It is not, and it can improve ride comfort.

The nose when owner ring, FIG. 3, the trailing arm in the arrow to the horizontal load (橫荷重) as indicated by F _B acts on the wheel (5), by the lateral load F _B bush 12 parts ( The load Fb acts as a forward displacement of 2).

However, in the illustrated embodiment of the present invention, since the spring characteristic of the bush 12 is set to be rigid with respect to the forward displacement as described above, the forward displacement of the trailing arm 2 is suppressed as much as possible. For this reason, the change of the toe angle of the wheel 5 resulting from the torsional deformation of the suspension frame 1 due to the front displacement of the trailing arm 2 is suppressed as much as possible, and the roughness stability of the automobile is increased accordingly.

In other words, the spring characteristics of the bush 12 are changed with respect to the two-way loads F _A and F _B loaded on the wheels 5 as the trailing arm 2 is shifted forward and rearward. By making the function (12) more effective, it is possible to improve the ride time and the steering stability of the vehicle together.

Furthermore, in this embodiment, as described above, the swing axes L ₁ and L ₁ of the torsion beam 3 are respectively inclined to retreat toward both end portions of the vehicle body in the horizontal plane, but in this case, the swing axes L ₁ , As compared with the case where the direction of L ₁ is set to be parallel to the axis line of the torsion beam 3, the center of rotation as the whole of the suspension frame 1 can be closer to the axle line L ₂ . For this reason, the moment of rotation center circumference loaded on the suspension frame 1 according to the lateral load F _B at the time of coowning is reduced as much as possible, and the wheel 5 due to the torsional deformation of the suspension frame 1 is reduced. Toe angle changes are inhibited if possible. In other words, the spring characteristics of the front displacement and the rear displacement as described above, in that the change of the toe angle of the wheel 5 during co-owning is suppressed as much as possible to increase the often stability of the vehicle. As shown in the illustrated embodiment, the bushes 12 formed to be different from each other are applied to the rear wheel suspension device having the suspension frame 1 in which the oscillation axis of the torsion beam 3 is inclined rearward by facing both ends of the vehicle body. Most suitable.

As is apparent from the above description, the rear suspension of a vehicle of the present invention sets the spring characteristic of the bush which can be interposed between the trailing arm and the vehicle body so as to be smooth in the direction in which the trailing arm is displaced toward the front side of the vehicle body. As a result, the effect of absorbing the shock load in the rapid starting of the vehicle, etc., and the suppression of the change of the toe angle of the wheel during the coordination of the vehicle are promoted, resulting in good feeling and control when riding in the vehicle. The effect that stability is improved can be acquired.

Claims (1)

A pair of left and right trailing arms 2 arranged in front and rear directions, and the front end portion thereof is freely swinged up and down with respect to the vehicle body, and the rear end portion is supported so as to freely rotate the wheel. And rear wheel suspension of a vehicle having a rear wheel suspension frame 1, which is disposed in the left and right directions of the vehicle body and whose both ends are constituted by a torsion beam 3 connected to an intermediate portion of the trailing arm 2; In the apparatus, a bush 12 having elasticity is interposed between the trailing arm 2 and the vehicle body. The spring 12 has a spring characteristic, and the trailing arm 2 is rearward of the vehicle body. A rear wheel suspension apparatus for a vehicle, characterized in that it is hard in a direction displacing to the side, and is set to be smooth in a direction displacing the trailing arm (2) to the rear side of the vehicle body.