JPS62216808A - Wheel supporting device - Google Patents

Abstract

PURPOSE:To relieve a load on an actuator, by a method wherein, in a title device which is capable of controlling wheel alignment, a suspension arm is rotatably supported to a car body, and the actuator is coupled thereto through an eccentric cam plate and a cam guide. CONSTITUTION:When an actuator 150 is actuated through the feed of an oil pressure to the actuator 150, an eccentric bolt 6 is rotated, an eccentric cam plate 8 is supported to a cam guide 9 for rotation, and is held in place. With this state, a vehicle is run. Thus, even if a load is applied on wheels resulting from rapid acceleration, the load is transmitted to a cross member 3 through a suspension arm 1, and the eccentric bolt 6, and a high load is prevented from application on the actuator. This constitution enables relief of a load on the actuator.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a wheel support device for a motor vehicle. In some cases, the wheel support device of the present invention is structured to support the wheel alignment of a wheel in a controllable manner.

[Conventional technology]

Conventionally, as a structure for supporting wheel alignment in a controllable manner, for example, Japanese Utility Model Application No. 60-1388
．． There is something like the one described in Publication No. 15. however,
This conventional support device has a structure in which a device for driving the suspension arm is directly interposed at a connecting portion between the suspension arm and the vehicle body. Therefore, there is a problem in that the force applied to the wheel is directly transmitted to the drive actuator via the suspension arm.

That is, in this conventional structure, the force applied to the suspension arm supporting the wheel during braking or acceleration is directly transmitted to the suspension arm drive actuator. Therefore, it has been difficult to maintain the drive actuator at a neutral point, that is, at a position where the wheels keep moving straight. In order to hold the actuator at the neutral point, it was necessary to constantly apply a large amount of pressure to the actuator and maintain that state. This not only means that maintenance of the actuator is difficult, but also inevitably increases the size and weight of the actuator.

[Problem that the invention seeks to solve]

The present invention has been devised in view of the above points, and its technical problem is to prevent a large load from being directly applied to an actuator that swings a suspension arm relative to a vehicle body.

[Means for solving problems]

In order to achieve the above-mentioned object, in the present invention, a support shaft is disposed at the connection portion between the suspension arm and the vehicle body.

This support shaft is rotatable with respect to the suspension arm, and is also rotatable with respect to a support guide portion formed on the vehicle body side. A cam plate that rotates integrally with the support shaft is formed on a part of the support shaft. Also,
This cam plate is rotatably supported by a cam guide formed in the support guide section. moreover,
The center of rotation of the cam plate is eccentric to the central axis of the support shaft. The actuator is one that rotationally drives the support shaft.

[Effect]

With the above configuration, the driving force of the actuator is first transmitted to the movable portion of the support shaft as rotational driving force.

When the support shaft rotates by the connecting member to the suspension arm, the cam plate also rotates within the cam guide at the same time. Since the cam plate and the support shaft are eccentric, the amount of eccentricity results in a change in the relative position of the cam guide and the suspension arm. In other words, by rotating the support shaft portion using the actuator, the relative position between the suspension arm and the cam guide, that is, the support guide portion changes, and the suspension arm swings relative to the vehicle body.

In the support device of the present invention, the load applied from the wheels is transmitted to the support shaft portion through the suspension arm. In the device of the present invention, since the actuator is used only to rotate the support shaft, the external force from the wheel side transmitted to the support shaft is not directly transmitted to the actuator.

〔Example〕

An embodiment of the apparatus of the present invention will be described below with reference to the drawings.

FIG. 1 shows an overall view of an automobile to which the device of the present invention is installed. The rear wheel 2 and the rear wheel 102 are the suspension arm 1,
It is connected to the cross member 3 via 101. Note that the cross member 3 is fixed to the vehicle body here. The suspension arm 1, the suspension arm 101, and the cross member 3 are connected to an outer connecting portion 131. as shown in FIG.
Inner connecting portion 134. Inner connecting portion 133 and outer connecting portion 1
30. The actuator according to the present invention is shown in FIG.
33 and the inner connecting portion 134 portion.

FIG. 3 is a diagram schematically showing this connecting portion.

That is, the suspension arm l is connected to the cross member 3 via the outer connecting portion 130.

A bolt 4 passes through a support connecting portion 350 formed at the end of the suspension arm 1, and the end of the bolt 4 is fixed with a nut 5. Since the bolts 4 pass through bolt holes formed in the outer support guide part 135 and the outer support guide part 136 at the same time, the support connection part 350 is connected by the bolts 4. Similarly, the outer connecting portion 131 is also fixed by the bolt 4.

On the other hand, the inner connecting portion 133 and the inner connecting portion 134 are connected by a bolt, and the bolt is an eccentric bolt 6. Then, the eccentric bolt 6 is rotated by the actuators 150 of the power cylinders 10 and 11.

FIG. 4 is a partially enlarged view of FIG. 2 taken along the diagonal line and viewed from direction A. The end of the eccentric bolt 6 has a cam plate 8
is formed to rotate together with the eccentric bolt 6.

The cam plate 8 is held by a cam guide 9. Therefore, when the eccentric bolt 6 rotates, the cam plate 8 also rotates within the cam guide 9 at the same time. Therefore, since the cam guide 9 and the inner support guide part 137 are integrally connected, when the eccentric bolt 6 rotates, the relative positions of the inner support guide part 137 and the eccentric bolt 6 will be displaced. Note that this structure has been conventionally employed for position adjustment (toe-in adjustment) of the suspension arm 1 and the suspension arm 101.

Adjustment scales are formed on the periphery of the cam plate 8, and support points are also provided on the inner support guide portion 137 at positions facing the scales. Therefore, by aligning these scales, the center position of the suspension arm 1 can be adjusted.

FIG. 5 is a sectional view showing this inner connecting portion 133 portion. In other words, the inner support guide portion 13 is provided on the cross member 3 side.
7 and an inner support guide part 138 are integrally formed, and a power cylinder mounting cloth stay 1 is attached to the cross member 3.
4 is fixed.

Further, an actuator 150 is fixed to the power cylinder mounting cloth stay 14 with bolts or the like (not shown). Inside the actuator 150 formed at the end of the suspension arm 1, an inner cylindrical ring 23 is disposed with an inner rubber bush 22 interposed therebetween. Furthermore, an eccentric bolt 6 is rotatably supported within the cylindrical ring inner side 23.

In particular, the support shaft portion 60 of the eccentric bolt 6 is attached to the inner side 23 of the cylindrical ring.
It is placed so as to directly face the. Further, a support shaft chamfered portion 6e is formed at the end of the eccentric bolt 6, and a cam plate 8 is disposed at this support shaft chamfered portion 61 portion. That is, the cam plate 8 is formed to rotate together with the eccentric bolt 6 by the support shaft chamfered portion 61. This cam plate 8 is fixed to an eccentric bolt 6 by a nut 5.

A cam guide 9 is formed to protrude from the inner support guide portion 138, and a journal ring 12 is disposed on the inner surface of the cam guide 9. That is, journal ring 12
is arranged on the outer surface of the cam plate 8. Therefore, the cam plate 8 is rotatably supported by the cam guide 9 via the journal ring 12. Bolt through holes are formed in the inner support guide portion 138 and the inner support guide portion 137, respectively, and the bolt through holes in the inner support guide portion 137 are elongated holes 139 in the cross member guide portion. A cam plate 351 is formed on the eccentric bolt 6 on the inner support guide portion 137 side. This cam plate 351 is integrally fixed to the eccentric bolt 6, and therefore, the cam plate 351 rotates together with the eccentric bolt 6. In addition, the inner support guide portion 137
A cam guide 352 is formed in the cam guide 352, and the cam plate 351 is rotatably supported by the cam guide 352. The journal ring 12 is disposed between the cam plate 351 and the cam guide 352, and facilitates its rotation.

Therefore, in this state, the load from the rear wheel 2 and rear wheel 102 side is transmitted from the support connection part 350 of the suspension arm 1 to the support shaft part 60 via the rubber bush inner side 22 and the cylindrical ring inner side 23. The load transmitted to the inner side 23 of the cylindrical ring is transmitted from the cam plate 8 and the cam plate 351 to the cam guide 9 and the cam guide 352, respectively,
Next, the inner support guide part 138 and the inner support guide part 1
37 to the cross member 3.

At the end of the eccentric bolt 6, there is a connecting portion 35 as shown in FIG.
3 protrudes in the radial direction. The connecting portion 353 is rotatably connected to the bar 17 via the shaft 16. Further, the bar 17 is connected to a joint 19 via the shaft 16. Note that the shaft 16 is held by a snap ring 18.

The joint 19 is connected to the piston 21. The joint 19 and the piston 21 are connected by the pin 2.
done by 0.

Next, the actuator 150 will be explained based on FIG. 6. A stopper 24 and a sealing ring 26 are press-fitted into the power cylinder 10.

Note that seals are held between the sealing ring 26 and the power cylinder 10 and between the stopper 24 and the power cylinder 10 by large O-rings 29, respectively.

A piston 21 is slidably disposed within the sealing ring 26 and the stopper 24. Oil-tightness is maintained between the stopper 24 and the piston 21 and between the sealing ring 26 and the piston 21 by small O-rings 28, respectively. Small O-ring 28 is backup ring 31
is held by.

A cap 32 is attached to the end of the power cylinder 10. The piston 21 has a large diameter portion 2 in its center.
11 is formed, and this piston large diameter portion 211 is slidably disposed within the power cylinder 10. The piston large-diameter portion 211 and the power cylinder 10 are kept oil-tight by a piston O-ring 30. A spring 2 is installed between the piston large diameter portion 211 and the stopper 24.
5 is disposed, and this spring 25 presses the piston large diameter portion 211 in the right direction in the figure. Similarly, a spring 25 is disposed between the piston large diameter portion 211 and the sealing ring 26.
5, the piston large diameter portion 211 is pushed leftward in the figure.

Inside the power cylinder 10 are a control pressure chamber 40 and a control pressure chamber 4.
1 is formed. That is, the control pressure chamber 40 is formed by the outer surface of the piston 21, the side surface of the large diameter portion 211 of the piston, the inner surface of the stopper 24, and the inner surface of the power cylinder 10. Similarly, the control pressure chamber 41 includes the side surface of the piston large diameter portion 211, the side surface of the sealing ring 26, the inner surface of the power cylinder 10, and the piston 2.
1 outer surface.

The power cylinder 10 has a control pressure port 38 and a control pressure port 39.
are formed and communicate with the control pressure chamber 40 and the control pressure chamber 41, respectively. The hydraulic pressure introduced into the control pressure port 38 and the control pressure port 39 is controlled by an electromagnetic switching valve 37.

The electromagnetic switching valve 37 is connected to a control passage 371. Control passage 372. It has a control passage 373 and a control passage 374, the control passage 373 communicating with the control pressure port 38, and the control passage 374 communicating with the control pressure port 39.

The pump 34 sucks oil in the reservoir tank 33 and discharges it under high pressure.

A check valve 35 and an accumulator 36 are installed in the middle of the discharge passage.
Therefore, the oil discharged from the pump 34 is controlled at a pressure above a certain level to the passage 371.
will be introduced in On the other hand, the control passage 372 communicates with the reservoir tank 33.

Next, the operation of the above-mentioned constituent device will be explained.

FIG. 6 shows a state in which no voltage is applied to the electromagnetic switching valve 37. In this state, the control passage 373 and the control passage 37
4 is in communication with the control passage 372.

Therefore, low-pressure oil in the reservoir tank 33 is introduced into the control pressure port 38 and the control pressure port 39 via the electromagnetic switching valve 37. Therefore, the oil pressures in the control pressure chamber 40 and the control pressure chamber 41 are equal. Therefore, the piston large diameter portion 211 is held at the center position within the power cylinder 10 by the setting force of the spring 25. This fluctuation of the piston large diameter portion 211 causes the piston 21. Bar 17. It is transmitted to the eccentric bolt 6 via the connecting portion 353. That is, in this state, the eccentric bolt 6 rotates to the position shown in FIG. 6 and is held in that state. In this state, the wheels are held in the direction of travel. Here, even if a load is applied to the wheel during sudden acceleration or sudden braking, the load is transmitted to the cross member 3 via the suspension arm 1 and the eccentric bolt 6, so the load transmitted to the actuator 150 side is very small. . Therefore, even if the position of the piston large diameter portion 211 is simply held by the spring 25, the actuator 150 can continue to maintain the position well.

Next, FIG. 7 shows a state in which a negative voltage is applied to the electromagnetic switching valve 37. In this state, accumulator 3
A predetermined high pressure on the 6 side is introduced into the control pressure port 38 via the control passage 371° and the control passage 373. On the other hand, the pressure inside the reservoir tank 33, that is, low pressure is supplied to the control pressure port 39.

Therefore, the pressure inside the control pressure chamber 40 becomes higher than the pressure inside the control pressure chamber 41, and based on the pressure difference, the piston large diameter portion 21
1 moves to the right in the figure.

This displacement of the piston large diameter portion 211 is transmitted to the eccentric bolt 6 via the bar 17 and the connecting portion 353.

At this time, since the eccentric bolt 6 is rotatably supported by the cam guide 352 and the cam guide 9 via the cam plate 351 and the cam plate 8, the rotation of the eccentric bolt 6 causes the center (in FIG. 6) and the centers of the cam plate 8 and the cam plate 351 will be displaced. That is, in the state shown in FIG. 7, the central axis of the eccentric bolt 6 is aligned with the cam plate 8 and the cam plate 35.
It is displaced to the right in the figure from the central axis of No. 1.

This means that the relative position of the suspension arm 1 supported by the eccentric bolt 6 and the inner support guide part 137 and the inner support guide part 138 that support the cam plate 8 and the cam plate 351 is displaced. For example, the right rear wheel is in a toe-in state, which is the same state as when the vehicle is steered to the left.

FIG. 8 shows a state in which a positive voltage is applied to the electromagnetic switching valve 37. In this case, the electromagnetic switching valve 37 switches and the control pressure port 3
The low pressure in the reservoir tank 33 is introduced into the control pressure port 8, and the high pressure from the accumulator 36 is introduced into the control pressure port 39. Therefore, the piston large diameter portion 211 is displaced to the left in the figure. Due to this displacement, the piston 21. Bar 17 and connecting part 35
3, the displacement is transmitted to the eccentric bolt 6.

In this case, the state shown in FIG. 7 described above is reversed,
The center axis of the eccentric bolt 6 is displaced from the center axes of the cam plate 8 and the cam plate 351 to the left in the figure. Therefore, the relative positions of the cross member 3 and the suspension arm 1 are displaced. In other words, in this state, the right rear wheel moves to the toe-out side, resulting in the same state as when the vehicle is steered to the right.

As described above, the voltage applied to the electromagnetic switching valve 37 is positive,
By switching to a negative state or a state in which no voltage is applied, the left and right suspension arms 1 and the suspension arm 101 can be independently controlled to swing. Therefore, by switching the electromagnetic switching valve 37, the steering performance of the automobile can be significantly improved.

The apparatus according to the above embodiment has the following excellent effects.

That is, in the above example, the eccentric bolt 6 and the cam plate 8
Since the length of the connecting portion 353, that is, the length between X and Y is larger than the variation with respect to the central axis of the cam plate 351, the principle of leverage acts. Therefore, even with a relatively small force generated in the piston 21, the eccentric bolt 6 can be easily rotated. Therefore, pump 3
The function of the actuator 150 can be achieved satisfactorily even if the pressure generated by the actuator 4 is not very large.

This also means that the force transmitted from the eccentric bolt 6 side to the piston 21 via the connecting portion 353 and the bar 17 becomes extremely small. Therefore, rear wheel 2 and rear wheel 1
Even if a large force is applied to the suspension arm 1 and the suspension arm 101 from the 02 side, it is possible to maintain the position of the eccentric bolt 6 well.

Furthermore, since the use of the cam plate 8 and the cam plate 351 at the end of the eccentric port 6 has been used for adjusting the suspension arm 1 and the suspension arm 101 in the past, the present invention can be adopted without making any major changes to the vehicle side. It has this effect.

Further, since the actuator 150 does not need to be located in a direction that directly presses the suspension arm 1 and the suspension arm 101, the degree of freedom in the arrangement position of the actuator 150 is extremely increased. That is, it becomes possible to attach the actuator 150 to the most desirable part of the vehicle.

Note that, although the above-mentioned example shows a desirable embodiment of the present invention, various other modifications can be made to the present invention.

For example, regarding the spring 25 for holding the intermediate position,
In addition to the coil springs described above, various other springs such as temporary springs may be used, and elastic bodies such as rubber may also be used.

Furthermore, in the above example, the eccentric bolt 6 and the actuator 1
50, the power is transmitted through the connecting portion 353, but a power transmitting mechanism such as a bevel gear or the like may be used for the connecting portion 353. Furthermore, although a hydraulic piston is used as the actuator in the above example, it is also possible to employ other actuators such as an electric motor and a hydraulic pump.

In addition, the outer diameters of the cam plate 8 and the cam plate 351 are circular in the above example, but it is of course possible to use shapes other than circular as long as they are cam-shaped with eccentricity. be.

Furthermore, in the above example, the suspension arm l and the suspension arm 101 are so-called trailing arm type support structures as shown in FIG. It is possible to apply the device of the present invention to the connection portion with.

〔Effect of the invention〕

As explained above, in the device of the present invention, the driving force of the actuator is transmitted to the support shaft via the cam plate, and the suspension arm and the vehicle body are connected by the support shaft, so a large load is placed on the support shaft. Even if the load is applied, the load is not directly transmitted to the actuator. Therefore, there is an excellent effect that a large driving force is not required for the actuator.

[Brief explanation of drawings]

Fig. 1 is a perspective view showing the overall structure of an automobile to which the device of the present invention is applied, Fig. 2 is an enlarged perspective view of the main part of Fig. 1, and Fig. 3 is a front view showing the state in which the device of the present invention is installed. FIG. 4 is a front view showing the cam ram part of the device of the present invention, FIG. 5 is a sectional view showing the support shaft and actuator part shown in FIG. 4, and FIG.
7 and 8 are sectional views showing the actuator shown in FIG. 5. FIG. 1... Suspension arm, 101... Suspension arm, 2... Rear wheel, 102... Rear wheel,
130...Outer connection part, 131...Outer connection part, 1
33... Inner connecting portion, 134... Inner connecting portion, 8.
...Cam plate, 6...Eccentric bolt, 150...
actuator. Representative Patent Attorney Takashi Okabe Figure 4

Claims (1)

[Claims] a suspension arm that rotatably supports a wheel; a support shaft portion rotatably disposed at an end of the suspension arm; a support guide portion formed on the vehicle body side that rotatably supports the support shaft portion; a cam plate disposed integrally with the support shaft portion and eccentric to the support shaft portion; a cam guide formed on the support guide portion and rotatably supporting the cam plate; and a cam guide rotatably driving the support shaft portion. A wheel support device comprising an actuator.