JP2003267021A - Strut type suspension device - Google Patents

Abstract

(57) [Problem] To provide a strut type suspension device capable of effectively reducing the side force of a suspension with a compact configuration that does not impose any layout restrictions. SOLUTION: A coil spring 1 and a shock absorber 2 inserted in a space inside the coil spring 1 are provided.
And an axle 5 attached to the outer cylinder 2b of the shock absorber, a column arranged in a vertical direction inclined inward of the vehicle, and an upper end of the column is swingably supported by the vehicle body, and In the strut type suspension device in which the lower end is pivoted to the outer end position of the lower link 6, between the lower spring seat 4 supporting the winding lower end of the coil spring 1 and the shock absorber outer cylinder 2b.
An elastic displacement mechanism 8 or a slide displacement mechanism 18 for displacing the lower spring seat 4 to the outside of the vehicle by a spring reaction force during a suspension stroke accompanying the bounce of the tire 7 is provided.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention belongs to the technical field of strut type suspension devices, which are often used in passenger cars, because of the advantages that the setting of the wheel alignment is accurate and the change is small, and the number of parts is small and the weight is light. .

[0002]

2. Description of the Related Art Due to the structure of a strut type suspension device, the front and rear force and the left and right force acting on the axle member are taken up by the shock absorber, so that a large side force acts on the sliding portion of the piston of the shock absorber. There is. This side force causes friction (sliding friction resistance) in the suspension, which makes it impossible to ensure a smooth shock absorber stroke, resulting in a reduction in riding comfort and steering stability performance.

This side force is disclosed, for example, in Japanese Patent Laid-Open No.
It is known that this can be reduced by arranging the coil spring offset from the shock absorber as described in Japanese Patent Publication No. 86125.

[0004]

However, in the conventional strut type suspension device, the coil spring is arranged so as to be largely offset with respect to the shock absorber so as to achieve zero side force. Therefore, there is a problem that the side force of the suspension cannot be canceled sufficiently when the offset amount of the coil spring with respect to the shock absorber cannot be sufficiently obtained due to various design restrictions. For example, when it is desired to secure a large vehicle interior space with a limited vehicle width, there is a design requirement that the space occupied by the tire house in which the suspension is arranged be kept as small as possible.

The present invention has been made in view of the above problems, and provides a strut type suspension device capable of effectively reducing the side force of a suspension by a compact structure that does not impose restrictions on layout. The purpose is to provide.

[0006]

In order to achieve the above object, in the present invention, in a strut type suspension device, a wheel of a wheel is provided between a lower spring seat supporting a winding lower end portion of a coil spring and a shock absorber outer cylinder. Lower spring seat displacement means is provided for displacing the lower spring seat to the outside of the vehicle by the spring reaction force during the suspension stroke accompanying the bound.

Here, the spring seat displacement means is
For example, an elastic displacement mechanism that displaces the lower spring seat outside the vehicle by elastically deforming it with the spring reaction force at the time of bound, or a lower spring seat displaces outside the vehicle by sliding with the spring reaction force when bound. A means for displacing the lower spring seat to the outside of the vehicle by utilizing the spring reaction force at the time of bouncing, such as a slide displacement mechanism.

[0008]

According to the present invention, when the lower spring seat is displaced to the outside of the vehicle by the spring reaction force at the time of bouncing, the inclination of the spring axis of the coil spring changes, and the spring axis becomes the lower link axis. It is possible to control so that it approaches the intersection with the tire vertical line passing through the contact point of the tire, or almost passes through the intersection.

Therefore, compared to the offset arrangement of the shock absorber and the coil spring, the side force of the suspension which causes friction can be effectively reduced by the compact structure which does not impose restrictions on layout.

[0010]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, an embodiment for realizing a strut-type suspension device of the present invention will be described with reference to claims 1 and 2.
A first embodiment corresponding to the invention according to claims 2 and 3, and claim 1.
The description will be made based on the second embodiment corresponding to the inventions according to the fourth and fifth aspects.

(First Embodiment) First, the structure will be described. FIG. 1 is a front view showing a strut type suspension device (when normal) of the first embodiment, and FIG. 2 is a front view showing a strut type suspension device (when bound) of the first embodiment.

In FIG. 1, S1 is a strut type suspension device of the first embodiment, 1 is a coil spring, and 2 is a coil spring.
Is a shock absorber, 2a is a piston rod, 2b is a shock absorber outer cylinder, 3 is an upper spring seat, 4 is a lower spring seat, 5 is an axle (axle member), 6 is a lower link (lower link member), and 7 is a tire ( Wheels) and 8 are elastic displacement mechanisms (lower spring seat displacement means).

In FIG. 1, 10 is a strut axis (= shock absorber axis), 11 is a spring axis, 12 is a bush axis, 13 is a lower link axis, and 14 is a shaft.
Is the tire vertical line.

Further, in FIG. 1, Pg is the tire ground contact point, Plb is the vehicle body side pivot of the lower link 6, Pla is the axle side pivot of the lower link 6, Pdu is the strut upper mount point, and Psu is the center of the upper spring seat 3. A point, Psl is a center point of the lower spring seat 4, and Po is an intersection of the lower link axis 13 and the tire vertical line 14 passing through the tire ground contact point Pg.

Strut type suspension device S1
Is a coil spring 1, a shock absorber 2 inserted in an inner space of the coil spring 1, an axle 5 attached to a shock absorber outer cylinder 2b,
The columns (struts) having the above are arranged in a vertical direction in which the upper ends of the columns are slightly inclined inward of the vehicle.

Then, the upper end of the column (= upper end of the piston rod 2a constituting the shock absorber 2) is swingably supported by a vehicle body (not shown) via an elastic body (strut upper mount point Pdu), and the lower end of the column. It is configured by pivoting (a lower end of an arm portion extending below the axle 5) to an outer end position of the lower link 6 (an axle-side pivot Pla).

FIG. 3 is a cross-sectional view showing the elastic displacement mechanism 8 in the strut type suspension device S1 of the first embodiment, and FIG. 9 is the elastic displacement of the strut type suspension device S1 of the first embodiment as viewed in the direction of arrow A in FIG. The elastic displacement mechanism 8 is a view showing a mechanism 8 between the lower spring seat 4 supporting the winding lower end portion of the coil spring 1 and the shock absorber outer cylinder 2b at the time of a suspension stroke accompanying the bounding of the tire 7. Is a displacement means for displacing the lower spring seat 4 to the outside of the vehicle by a spring reaction force.

As shown in FIGS. 3 and 4, the elastic displacement mechanism 8 includes a bush inner cylinder 8a fixed to the shock absorber outer cylinder 2b by welding or the like, and a bush fixed to the lower spring seat 4 by welding or the like. An outer cylinder 8b and a bush rubber 8c (elastic body) fixed by vulcanization adhesion or the like are provided between the bush outer cylinder 8b and the bush inner cylinder 8a.

As shown in FIG. 3, the bushing axis 12 of the elastic displacement mechanism 8 is inclined toward the inside of the vehicle with respect to the strut axis 10 and above the bushing axis 12 toward the outside of the vehicle. Is inclined to. That is,
The strut axis 10 and the bush axis 12 have an inclination angle θ.
It is set to intersect at 1.

Further, the bush rubber 8c of the elastic displacement mechanism 8 has a curls 8 for promoting elastic deformation inward of the vehicle.
d is provided.

Next, the operation will be described.

[Optimal Layout of Offset Coil Spring] Strut suspension S of the first embodiment
An optimum layout in the case of the separation type offset coil spring as in No. 1 will be described.

First, FIG. 5A shows a two-dimensional model of a strut-type suspension using an input separation type upper insulator. In FIG. 5 (a), Pg; tire ground contact point Plb; lower link body side pivot Pla; lower link axle side pivot Pdu; strut upper mount point Psu; upper spring seat center point Psl; lower spring seat center Point Po: The intersection of the lower link axis and the tire vertical line passing through the tire ground contact point Pg.

FIG. 5B shows side forces F1 and F2 acting on the shock absorber in the input separation type upper insulator. That is, when the force Fu in the right direction in the drawing acts on the strut upper mount point Pdu, the side force F1 in the left direction in the drawing acts on the guide bush position of the shock absorber piston rod (position L1 from the strut upper mount point Pdu). ,
At the piston position of the shock absorber (position at a distance L2 from the strut upper mount point Pdu), the side force F2 on the right side of the drawing works, and the side forces F1 and F2 are opposite to each other.

Further, as shown in FIG. 6, the symbols of the geometrical parameters used in the following description are as follows: θ: angle θd formed by the vertical line and straight line Pdu-Po; angle θs formed by the vertical line and spring axis line; Angle φ between vertical line and strut axis; angle between horizontal line and lower arm axis (= lower link) a; distance between point Po and point Pa b; distance between point Po and point Pb c; between spring axis and point Pdu Distance L1; Point Pdu to guide bush distance L2; Point Pdu to piston distance. However, b is a positive value when Pb is lower than Po and a negative value when Pb is higher. c is positive when the spring axis is outside the vehicle with respect to Pdu, and negative inside.

The process of deriving the side forces F1.F2 will be described below. As shown in Fig. 7, there are four external forces acting on the struts: ground load Fg, link axial force FL, spring force reaction from the vehicle body Fs, lateral force Fu on the upper mount.

Considering the balance of moments of the entire strut with reference to FIG. 8, the ratio of the horizontal components of the respective forces Fu, FL, Fs is Fu (cosθd): FL (cosφ): Fs (cosθs) = b: (A + b): a Fu (cos θd) = Fs (b / a) sin θs FL (cosφ) = Fs (1 + b / a) sin θs (1)

Next, the balance of the forces of the entire struts will be considered. Applying the condition of Eq. (1) to the condition that the vector sum of forces becomes zero, Fig. 9 is obtained. In this FIG. 9, Fg + Fu (sinθd) + FL (sinφ) = Fs (cosθs) (2) holds from the balance of the forces in the vertical direction.

Using the equation (1) again, By (3), the reaction Fs of the spring force from the vehicle body and the lateral force Fu applied to the upper mount are obtained.

Next, the balance of the piston rod will be considered. As shown in FIG. 5B, three forces of side forces F1 and F2 and a lateral force Fu act on the piston rod, which are perpendicular to the piston rod. These powers
By the balance of F1, F2, Fu and moment, ... (4). Therefore, by substituting equation (3) into equation (4), The side forces F1 and F2 can be calculated from (5).

Further, according to the equation (4), it is sufficient to set Fu = 0 in order to set F1 = F2 = 0. Since the lateral force Fu is expressed by the above equation (3), b = 0 for Fu = 0.
Must be This is the spring axis
It means passing through Po.

Next, considering the entire strut, Fu = 0
However, in order to keep the balance, it is necessary that Fs, FL, and Fg intersect at one point. That is, the spring axis may pass through the point Po.

In the case of the separation type, as described above, the side force is mechanically fixed regardless of the position of the upper seat.
F1 and F2 can be zero. However, if the center of the upper seat is separated from the strut upper mount, in the strut assembly state before being assembled to the vehicle, as shown in FIG. 10, the rubber insulator is bent to tilt the upper seat. As a result, it becomes difficult to assemble it to the vehicle body, and the bump rubber falls off. In order to prevent this state, set c = 0 ... (6). That is, the spring axis may pass through the strut upper mount point Pdu.

As a result of the above, the optimum layout for setting the side forces F1 and F2 of the separation type offset coil spring to zero is (a) the upper seat may be located at any position. (b) It suffices if the spring axis passes through the position of point Po. If the condition of is satisfied, the side forces F1 and F2 can be suppressed to zero.

[Side Force Reducing Action] First, in the strut suspension S1 of the first embodiment, as shown in FIG. 1, the spring axis 11 intersects at the normal point when the tire 7 is not displaced upward or downward of the vehicle. It is set to pass through Po. In other words, the layout is optimized so that the side forces F1 and F2 acting on the shock absorber 2 are zero.

When turning or running on uneven roads,
At the time of bouncing when the tire 7 is displaced to the upper side of the vehicle, as shown in FIG. 2, the shock absorber 2 contracts and the coil spring 1 contracts and deforms along with the stroke, and in the direction along the spring axis 11 from the center point Psu of the upper spring seat 3. Spring reaction force acts. On the other hand, the bush axis 12 of the elastic displacement mechanism 8 is the strut axis 1
It is set to intersect with 0 at an inclination angle θ1.

Therefore, when a spring reaction force acts from the lower spring seat 4 on the bush outer cylinder 8b, the bush outer cylinder 8b is displaced downward along the bush axis 12 toward the outside of the vehicle by the spring reaction force. As a result, the bush outer cylinder 8b is twisted counterclockwise with respect to the bush inner cylinder 8a while deforming the rubber bush 8c, and the vehicle outer side portion of the rubber bush 8c is stretched and deformed and the vehicle inner side portion is contracted and deformed. . With the deformation of the rubber bush 8c, the lower spring seat 4 fixed to the bush outer cylinder 8b moves to the outside of the vehicle.

In addition, since the rubber bush 8c of the elastic displacement mechanism 8 is provided with the curls 8d at the vehicle inner position in the left-right direction of the vehicle, the amount of shrinkage deformation of the inner portion of the rubber bush 8c at the time of bouncing. Is increased, and the amount of movement of the lower spring seat 4 outside the vehicle is increased as compared with the case where the curls 8d are not provided.

Due to the movement of the lower spring seat 4 to the outside of the vehicle, the center point Psl of the lower spring seat 4 also moves to the outside of the vehicle, and the spring axis 11 passing through the center point Psl.
Is directed to the inside of the vehicle according to the amount of movement of the lower spring seat 4 outside the vehicle.

In this way, by exerting the action of forcibly inclining the spring axis 11 toward the inside of the vehicle, the amount of movement of the lower spring seat 4 outside the vehicle is elastic so that the spring axis 11 passes through the intersection Po at the time of bouncing. Displacement mechanism 8
Can be controlled by. In other words, the side force acting on the shock absorber 2 of the strut suspension S1 at the time of bouncing.
It is possible to cancel F1 and F2.

As a result, the strut suspension S
The shock absorber 2 of No. 1 exhibits a smooth stroke operation that does not cause friction (sliding friction resistance). For example, it is possible to improve the ride comfort when traveling on uneven roads and to improve the steering stability performance when turning. it can.

Next, the effect will be described.

In the strut type suspension device S1 of the first embodiment, the effects listed below can be obtained.

(1) A pillar having a coil spring 1, a shock absorber 2 inserted in the inner space of the coil spring 1, and an axle 5 attached to a shock absorber outer cylinder 2b. In a longitudinal direction inclining inward of the vehicle, the upper end of the column is swingably supported by the vehicle body, and the lower end of the column is pivoted to the outer end position of the lower link 6 in the strut type suspension device. An elastic displacement mechanism for displacing the lower spring seat 4 to the outside of the vehicle by a spring reaction force during a suspension stroke caused by the bounding of the tire 7 between the lower spring seat 4 supporting the lower end of the winding and the shock absorber outer cylinder 2b. Since 8 is provided, the layout control is designed to control the inclination of the spring axis 11. Suspension side force F1, F by a compact configuration that does not give about
2 can be effectively reduced.

(2) Displacement means for the lower spring seat 4 includes a bush inner cylinder 8a fixed to the shock absorber outer cylinder 2b, a bush outer cylinder 8b fixed to the lower spring seat 4, a bush outer cylinder 8b and a bush. Inner cylinder 8a
An elastic displacement mechanism 8 having a rubber bush 8c fixed between and, and the bush axis 12 of the elastic displacement mechanism 8 is inclined inward from the strut axis 10 toward the inside of the vehicle. However, since the lower part of the bush axis 12 is inclined outward of the vehicle, the rubber bush 8
The elastic deformation of c causes the inclination of the spring axis 11 to intersect.
It is possible to control it so that it approaches Po, and the side force F1 and F2 of the suspension can be canceled when bounding.

(3) The elastic displacement mechanism 8 includes the rubber bush 8
Since the curls 8d are provided on the inner side of the vehicle of c, when the spring reaction force acts on the bush outer cylinder 8b, the lower spring seat 4 can be moved to the outer side of the vehicle more efficiently by the curling effect that promotes the contraction deformation. . As a result, at the time of bouncing, the spring axis 11 can be brought as close as possible to the line passing through the intersection Po, or can be made to substantially coincide with the line.

(Second Embodiment) A strut type suspension S2 of the second embodiment is an example in which a slide displacement mechanism 18 is provided as a lower spring seat displacement means.

First, the structure will be described. FIG. 11 is a front view showing a strut type suspension device (when normal) of the second embodiment, and FIG. 12 is a front view showing a strut type suspension device (when bound) of the second embodiment.

11 and 12, S2 is a strut type suspension device of the second embodiment, 18 is a slide displacement mechanism (lower spring seat displacement means),
The other structure is the same as that of the strut type suspension device S1 of the first embodiment shown in FIGS. 1 and 2, and therefore the corresponding structures are designated by the same reference numerals and the description thereof will be omitted.

13 to 16 are views showing the slide displacement mechanism 18, and the configuration of the slide displacement mechanism 18 will be described based on these drawings.

The slide displacement mechanism 18 is fixed to the shock absorber outer cylinder 2b by welding or the like, and a guide base 18a (guide member) having a guide groove 18c formed therein.
And a slide stay 18b (slide member) having one end fixed to the lower spring seat 4 and the other end slidably attached to the guide groove 18c of the guide base 18a.

As shown in FIG. 13 (a), the slide displacement mechanism 18 is set so that the guide groove 18c formed in the guide base 18a is inclined toward the vehicle lower side as it extends outward from the vehicle. . That is, the slide shaft 15 of the slide displacement mechanism 18 has the strut axis 10
And intersects with the axis line orthogonal to.

Further, as shown in FIGS. 13 (b) and 13 (c), the slide displacement mechanism 18 has inner surfaces of both ends of the guide grooves 18b formed in the guide base 18a,
Rubber bushes 18d and 18e (elastic bodies) are provided between the two ends of the slide stay 18b. The rubber bushes 18d and 18e have a sliding axial length of the rubber bush 18d arranged outside the vehicle.
The length is set longer than the length of the rubber bush 18e arranged inside the vehicle in the sliding axis direction.

A pair of roller slides are provided between the inner surfaces of both sides of the guide groove 18b formed in the guide base 18a and the both sides of the slide stay 18b in order to smoothly slide the slide stay 18b. Bearings 18f, 18f are interposed.

As shown in FIG. 14, the slide stay 18b includes a seat fixing portion 18b 'fixed to the lower spring seat 4 and a guide groove 18 of the guide base 18a.
Slide part 18b ″ slidably attached to c
And is integrally formed.

As shown in FIG. 15, the lower spring seat 4 is constructed to have a seat body portion 4a and a stay fixing portion 4b. The seat body portion 4a has an upper half of the seat fixing portion 18b '. Form a concave portion 4c that matches the shape,
The stay fixing portion 4b is formed with a recess 4d that conforms to the shape of the lower half of the seat fixing portion 18b '.

Then, the seat fixing portion 18b 'of the slide stay 18b is sandwiched by both recesses 4c and 4d, and the stay fixing portion 4b is fixed to the seat body portion 4a by welding or the like, as shown in FIG. The slide stay 18b and the lower spring seat 4 are fixed.

Next, the operation will be described.

[Side Force Reducing Action] First, as shown in FIG. 11, the strut suspension S2 of the second embodiment is set so that the spring axis 11 passes through the intersection Po at the normal time. In other words, the layout is optimized so that the side forces F1 and F2 acting on the shock absorber 2 are zero.

When turning or running on uneven roads,
At the time of bouncing when the tire 7 is displaced to the upper side of the vehicle, FIG.
2, the shock absorber 2 contracts and the coil spring 1 contracts and deforms along with the contraction stroke, and the lower spring seat 4 and the slide stay 1 of the slide displacement mechanism 18 are deformed.
A spring reaction force acts in the direction along the spring axis 11 from the fixed portion with 8b. On the other hand, the slide axis 15 of the slide displacement mechanism 18 is set to intersect the axis orthogonal to the strut axis 10 with an inclination angle θ2.

Therefore, when a spring reaction force is applied to the slide stay 18b from the lower spring seat 4, the slide stay 18b is moved toward the outside of the vehicle along the slide axis 15 by the component force of the spring reaction force in the slide axis direction. Slide to move. As a result, the slide stay 1 is deformed while contracting and deforming the rubber bush 18d.
The lower spring seat 4 fixed to 8b moves to the outside of the vehicle.

Due to the movement of the lower spring seat 4 to the outside of the vehicle, the center point Psl of the lower spring seat 4 also moves to the outside of the vehicle, and the spring axis 11 passing through the center point Psl.
Is directed to the inside of the vehicle according to the amount of movement of the lower spring seat 4 outside the vehicle.

In this way, by exhibiting the action of forcibly inclining the spring axis 11 toward the inside of the vehicle, the amount of movement of the lower spring seat 4 outside the vehicle is slid so that the spring axis 11 passes through the intersection Po at the time of bouncing. It becomes possible to control by the displacement mechanism 18. In other words, it is possible to cancel the side forces F1 and F2 acting on the shock absorber 2 of the strut suspension S2 at the time of bouncing.

As a result, the strut suspension S
The shock absorber 2 of No. 2 exhibits a smooth stroke operation that does not cause friction (sliding friction resistance). For example, the ride comfort is good when traveling on uneven roads, and the steering stability performance is improved when turning. it can.

Next, the effect will be described.

In the strut type suspension device S2 of the second embodiment, in addition to the effect of (1) of the first embodiment,
The effects listed below can be obtained.

(4) The displacement means of the lower spring seat 4 is fixed to the shock absorber outer cylinder 2b and the guide base 18a having the guide groove 18c is formed, and one end is fixed to the lower spring seat 4 and the other end is A slide displacement mechanism 18 having a slide stay 18b slidably attached to the guide groove 18c of the guide base 18a, and the slide displacement mechanism 18 is configured such that the guide groove 18c formed in the guide base 18a is outside the vehicle. Since the vehicle is inclined toward the lower side of the vehicle as it goes toward the vehicle, the inclination of the spring axis 11 can be controlled to approach the intersection Po by the sliding displacement of the slide stay 18b toward the outside of the vehicle. It is possible to maintain the state where forces F1 and F2 are canceled.

(5) The slide displacement mechanism 18 has inner surfaces of both ends of the guide groove 18b formed in the guide base 18a,
Since the rubber bushes 18d and 18e are provided between the both ends of the slide stay 18b, vibrations and operation noises generated when the slide stay 18b slides in the guide groove 18c are reduced (sound vibration reduction role). . When the slide stay 18b slides to the operating limit, it protects the guide base 18a and the slide stay 18b from damage and cushions impact (role of protection and cushioning). The spring stay causes the slide stay 18b, which has slid to the outside of the vehicle, to return to a normal position by the elastic restoring force (role of return spring). Can be achieved together.

Although the strut type suspension device of the present invention has been described above based on the first and second embodiments, the specific configuration is not limited to these embodiments, and the claims Modifications and additions of the design are allowed without departing from the scope of the invention according to each claim of the scope.

For example, in the embodiment, as the lower spring seat displacing means, the elastic displacing mechanism and the slide displacing mechanism are shown as an example. However, the concrete means are not limited to these mechanisms, and in short, they are generated at the time of bound As long as it is a means for displacing the lower spring seat to the outside of the vehicle by the spring reaction force, the other displacement mechanism using a link, a gear or the like may be adopted.

[Brief description of drawings]

FIG. 1 is a front view showing a strut type suspension device (in a normal state) of a first embodiment.

FIG. 2 is a front view showing a strut type suspension device (when bound) according to the first embodiment.

FIG. 3 is a longitudinal sectional view showing an elastic displacement mechanism in the strut type suspension device of the first embodiment.

FIG. 4 is a view from the direction of arrow A in FIG. 1 showing an elastic displacement mechanism in the strut type suspension device of the first embodiment.

FIG. 5 is a diagram showing a two-dimensional model of a strut type suspension device and a side force acting on a shock absorber.

FIG. 6 is a suspension schematic diagram showing symbols of geometry specifications and each geometry in the strut-type suspension device.

FIG. 7 is a diagram showing an external force acting on the entire strut suspension device.

FIG. 8 is a diagram showing a ratio of each force obtained from the balance of moments in the strut suspension device.

FIG. 9 is a diagram showing a balance of forces of struts in a strut-type suspension device.

FIG. 10 is a diagram showing a spring axis position in a strut suspension device.

FIG. 11 is a front view showing a strut type suspension device (in a normal state) of a second embodiment.

FIG. 12 is a front view showing a strut type suspension device of the second embodiment (at the time of bouncing).

FIG. 13 is a view showing a slide displacement mechanism in the strut type suspension device of the second embodiment.

FIG. 14 is a perspective view showing a slide stay of a slide displacement mechanism in the strut type suspension device of the second embodiment.

FIG. 15 is a side view showing a fixing portion between a slide stay and a lower spring seat in the strut type suspension device of the second embodiment.

FIG. 16 is a plan view showing a shock absorber, a slide stay, and a lower spring seat in the strut type suspension device of the second embodiment.

[Explanation of symbols]

S1 Strut type suspension device of the first embodiment 1 Coil spring 2 Shock absorber 2a Piston rod 2b Shock absorber outer cylinder 3 Upper spring seat 4 Lower spring seat 5 Axle (axle member) 6 Lower link (lower link member) 7 Tire (wheel) ) 8 elastic displacement mechanism (lower spring seat displacement means) 8a bush inner cylinder 8b bush outer cylinder 8c bush rubber (elastic body) 8d curling 10 strut axis (= shock absorber axis) 11 spring axis 12 bush axis 13 lower link axis 14 tire Vertical line 15 Slide axis S2 Strut type suspension device of the second embodiment 18 Slide displacement mechanism (lower spring seat displacement means) 18a Guide base (guide member) 18b Slide stay 8b (sliding member) 18c Guide groove Pg Tire grounding point Plb Body side pivot of lower link 6 Axle side pivot of lower link 6 Pdu strut Upper mount point Psu Upper spring seat 3 center point Psl Lower spring seat 4 center point Po The intersection of the lower link axis 13 and the tire vertical line 14 passing through the tire ground contact point Pg

Continued front page    (72) Inventor Yoshihiro Kawabe             Nissan, Takaracho, Kanagawa-ku, Yokohama-shi, Kanagawa Nissan             Inside the automobile corporation F-term (reference) 3D001 AA17 AA18 BA02 CA01 DA01                 3J069 AA50 CC34

Claims (5)

[Claims] 1. A column is vertically arranged with a coil spring, a shock absorber inserted in an inner space of the coil spring, and an axle member attached to an outer cylinder of the shock absorber. In the strut type suspension device in which the upper end of the column is swingably supported on the vehicle body, between the lower spring seat supporting the winding lower end portion of the coil spring and the shock absorber outer cylinder,
During the suspension stroke accompanying the bouncing of the wheels,
A strut type suspension device comprising lower spring seat displacement means for displacing the lower spring seat to the outside of the vehicle by a spring reaction force. 2. The strut type suspension device according to claim 1, wherein the lower spring seat displacement means includes a bush inner cylinder fixed to the shock absorber outer cylinder, and a bush outer cylinder fixed to the lower spring seat. An elastic displacement mechanism having an elastic body fixed between the bush outer cylinder and the bush inner cylinder, and the bush axis of the elastic displacement mechanism is located above the bush axis with respect to the shock absorber axis. A strut-type suspension device characterized by being inclined inward of the vehicle and being inclined outward of the vehicle at a lower portion of a bush axis. 3. The strut type suspension device according to claim 2, wherein the elastic displacement mechanism is provided with a currant on the vehicle inner side of the elastic body. 4. The strut type suspension device according to claim 1, wherein the lower spring seat displacement means is fixed to the shock absorber outer cylinder and has a guide member formed with a guide groove, and one end of the lower spring seat. And a slide member having the other end slidably attached to the groove of the guide member, and the slide displacement mechanism having a guide groove formed in the guide member. A strut-type suspension device, which is inclined toward the lower side of the vehicle as it goes toward the outside of the vehicle. 5. The strut-type suspension device according to claim 4, wherein the slide displacement mechanism includes elastic members between the inner surfaces of both end grooves of the guide groove formed in the guide member and the both end surfaces of the slide member. A strut-type suspension device characterized by being provided with.