JPS6230924B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a spring support device for a vehicle.

As a conventional spring support device for a vehicle, there is one shown in FIG. 1, for example. This is an example of a strut type front suspension in which a coil spring 1 and a shock absorber are installed on the same axis, and a cylinder tube (not shown in the figure), which forms a twin inch tube type shock absorber, is removably attached to the strut tube 3. Built-in. A piston (not shown) that divides the interior of the cylinder tube into an upper chamber and a lower chamber is loosely fitted into the cylinder tube, and the lower end of a piston rod 4 whose upper end protrudes outside the cylinder tube is fixed to this piston. There is. The lower end of the strut tube 3 is fixed to a steering knuckle 5 or the like.

Further, in the figure, 6 is a lower spring seat, and this lower spring seat 6 is fitted onto the outside of the strut tube 3 and fixed by welding. The coil spring 1 is compressed directly or via a rubber sheet or the like between an upper spring seat (not shown) externally fitted and fixed to the upper part of the piston rod 4. Furthermore, an inner cylinder (not shown) is fixed to the upper part of the atspa spring seat of the piston rod 4, and a mounting in is installed between the inner cylinder and the outer cylinder (not shown) fixed to the vehicle body with bolts and nuts. A simulator (not shown) is used. Thus, the upper end of the shock absorber to which the coil spring 1 is mounted is connected to the vehicle body side, which is the supported body, and the lower end of the shock absorber is connected to the road wheel side, which is the support body.

However, in such a conventional spring support structure for a vehicle, the lower spring seat 6 on the supporting body side or the upper spring seat on the supported body side and the coil spring 1 are in direct contact with each other, or the coil spring 1 is in direct contact with the lower spring seat 6 on the supporting body side, or a rubber sheet or the like is used. The structure was such that contact was made through the Therefore, not only when the lower spring seat 6 or Atsupa spring seat and the coil spring 1 are in direct contact with each other, but also when they are brought into contact via a rubber sheet, etc., the rubber sheet etc. The two are in rigid contact through a rubber sheet, etc., which is compressed by the spring force and becomes hard, and which is actually extremely hard. Therefore, when the frequency of vibration input from the supporting body side or the supported body side matches the natural frequency of the coil spring 1, the coil spring 1 resonates, and this causes a rough vibration in the direction of expansion and contraction of the coil spring 1. A dense portion and a dense portion are formed and move in the same direction, causing a so-called surging phenomenon. As a result, an unreasonable force is applied locally to the coil spring 1, which not only impairs ride comfort, but also causes vibrations caused by the surging phenomenon to be transmitted to the passenger compartment, resulting in poor quietness in the passenger compartment. .

Therefore, the applicant previously filed an application for a spring support device having a structure as shown in FIG. 2 (Utility Application No. 129147-1980, name of the invention: Spring support structure for vehicles). The spring support device shown in FIG. 2 is a spring support structure in which a coil spring 1 is interposed between a support body and a supported body, and the support body is supported by the support body. A disc spring 12 is interposed between at least one of the coil spring 1 and the coil spring 1. That is, the inner circumferential edge 12b of the disc spring 12 is seated on the disc spring receiving member 13 that is fitted onto and fixed to the strut tube 3, and the lower end of the coil spring 1 is seated on the seated spring receiving member 11. The peripheral edge 12a is seated. Then, the disc spring 12 is bent in advance by the dimension of the free height to be elastically deformed into a flat plate shape, and the spring constant of the disc spring 12 is made nonlinear, so that low frequency vibrations with relatively large amplitudes are input. When the coil spring 1 is
While the coil spring 1
High-frequency vibrations with relatively small amplitudes that are not attenuated by
2, it is absorbed and attenuated. In addition, in the figure, 10 is a lower spring receiving part, which is composed of a spring receiving member 11, a disc spring 12, and a disc spring receiving member 13.

Further, 7 is an Atsupa spring seat, 8 is a mounting insulator, and 9 is a vehicle body side plate.

However, in the prior art vehicle spring support device shown in FIG.
2, and the spring receiving member 11 and the disc spring receiving member 13 were in direct contact with each other.
Moreover, the disc spring 12 is made of spring steel and has a fairly high hardness, while the spring receiving member 11 and the disc spring receiving member 13 are made of structural steel and have a not so high hardness. For this reason, the disc spring 12 and both receiving members 11 and 13 rub against each other every time vibration is input, and there is a risk that the members rubbing against each other may seize. Therefore, it is necessary to lubricate the lower spring receiving portion 10 from the viewpoint of the durability of the device, but providing a device for holding or supplying lubricant requires an additional cost in addition to the spring support device. There was an inadequacy in that it took a long time.

This invention was made by focusing on the insufficiency of the prior art, and proposes a method in which a coil spring is interposed between the support and the supported object so that the supported object is supported by the support. In the spring support device, at least one of the support body or the supported body and the coil spring is elastically deformed into a flat elastic disc shape by bending by the free height dimension due to the load when the vehicle is stationary. A disc spring having a spring constant of By interposing a ring-shaped member that has a hardness close to that of a spring and has a shape that makes line contact with the disc spring, the load is received on the inside and outside of the disc spring, so that the disc spring and the support or cover are separated. The purpose is to significantly reduce the difference in hardness between the support and the support, thereby solving the above-mentioned inadequacies.

The present invention will be explained below based on the drawings.

3 to 8 show an embodiment of the present invention, and are views of a strut type front suspension in which a coil spring 1 and a shock absorber are provided on the same axis.

First, to explain the structure, 3 in Fig. 3 is a strut tube, and this strut tube 3
Inside, a cylinder tube (not shown) forming a twin inch tube type shock absorber is removably housed. The cylinder tube is filled with hydraulic fluid, and a piston (not shown) that partitions the inside of the cylinder tube into an upper chamber and a lower chamber is loosely fitted therein. The piston is provided with an orifice (not shown) that communicates between the upper and lower chambers, and when the piston moves up and down within the cylinder tube, a damping force is obtained by the flow resistance of the hydraulic fluid that passes through the orifice. The lower end of a piston rod 4 whose upper end projects outside the cylinder tube is fixed to this piston. and,
A steering knuckle 5 is fixed to the lower end of the strut tube 3, and a load wheel (not shown) serving as a support is fixed to a spindle 5a of the steering knuckle 5.

An upper spring seat 7 is fixed to the upper part of the piston rod 4, and the upper part of the upper spring seat 7 of the piston rod 4 is also engaged with the piston rod 4 via a mounting insulator 8 that engages with the mounting insulator 8. It is fixed to the vehicle body side plate 9. A coil spring 1 is interposed between the upper spring seat 7 and a lower spring receiving portion 10 fitted onto the strut tube 3.

The lower spring receiving portion 10 is shown in FIG.
As shown in the exploded and enlarged diagrams in Figures B to 8,
It consists of a spring receiving member 11, a ring-shaped member 15 on the outer circumferential side, a disc spring 12, a ring-shaped member 16 on the inner circumferential side, and a disc spring receiving member 13. , the spring receiving member 11, the disc spring 12, and the disc spring receiving member 13 are all ring-shaped.

Spring receiving member 1 shown in FIGS. 4A and B
1 is formed with a spiral spring seat 11b on which one end of the coil spring 1 is seated, and the other end surface is formed with an outer spring seat 11a into which the outer peripheral edge 12a of the disc spring 12 is fitted. Further, the outer spring seat 11a is provided with a ring groove 11c that continues in the circumferential direction.

The disc spring 12 shown in FIG. has a free height h. This disc spring 12 has a plate thickness t and a free height h
The spring force of the disc spring 12 is preferably set so that the ratio h/t of the disc spring 12 is approximately within the range of 1.2 to 1.5. It is set so that it flexes by the free height h and elastically deforms into a flat disc shape due to the load it receives.

The disc spring receiving member 13 shown in FIG. 8 has an inner diameter so that it can be fitted onto the strut tube 3, and an inner peripheral edge 12b of the disc spring 12 is fitted on the outside of one end surface. Spring seat 13a
Furthermore, a ring groove 13b continuous in the circumferential direction is provided in the inner spring seat 13a. Then, the disc spring receiving member 13 is externally fitted onto the strut tube 3 with the inner spring seat 13a facing upward, and these are fixed to the strut tube by welding or the like.

An outer ring-shaped member 15 shown in FIG. 5 and an inner ring-shaped member 16 shown in FIG.
In this example, the piano wire is formed by bending it into a ring shape, and it is preferable to cut out one place in the circumferential direction to form a C-shape from the viewpoint of ease of assembly. However, it may be continuous in an endless manner. Further, the cross-sectional shape of both ring members 15 and 16 is not limited to a circle but may be an ellipse or the like as long as it has a shape other than a rectangular shape. 11c or the ring groove 13b of the disc spring receiving member 13, the size is such that a part of the cross-sectional direction thereof is exposed from the surface of the outer spring seat 11a and the surface of the inner spring seat 13a, respectively.

In this way, the concave surface of the disc spring 12 faces upward, and its inner peripheral edge 12b is loosely fitted into the inner spring seat 13a of the disc spring receiving member 13, in which the ring-shaped member 16 is inserted into the ring groove 13b in advance, and the disc spring 12 is seated. At the same time, the outer peripheral edge 12a of the disc spring 12 is loosely fitted to the outer spring seat 11a of the spring receiving member 11, and is seated. As a result, one outer side surface of the disc spring 12 contacts the ring-shaped member 15, and the other inner side surface contacts the ring-shaped member 16.
After that, the spring seat 11b of the spring receiving member 11 and the Atsupa spring seat 7 are removed.
Both ends of the coil spring 1 are seated between them as shown in FIG. Then, fit the up spring seat 7 onto the piston rod 4 to cover the upper end of the coil spring 1, and
Furthermore, the mounting insulator 8 and the vehicle body side plate 9 are externally fitted onto the upper part of the piston rod 4 from above the upper spring seat 7. By tightening the nut 14 screwed into the male thread at the top of the piston rod 4, the coil spring 1 is held in a predetermined compressed state, and the upper spring seat 7 and mounting insulator 8 are tightened.
Then, tighten and fix the vehicle body side plate 9. In addition,
The edges of the disc spring 12 may be in contact with the ring-shaped members 15 and 16.

As a result, the upper end of the shock absorber to which the coil spring 1 is mounted is connected to the vehicle body side, which is a supported object, and the lower end of the shock absorber is connected to the road wheel side, which is a supporting body.

In addition, the hardness _HD of the disc spring 12 and the ring-shaped member 1
The relationship between hardness H _S of 5 and 16 is Rockwell hardness, and it is preferable to set it so that |H _{S −HD} |≦10, and in particular, set it so that H _S < _HD . is optimal. In this case, the disc spring 12 is better than the ring-shaped members 15, 1.
Since the ring-shaped members 15 and 16 are harder than the ring-shaped members 6, they wear out more quickly, and only the ring-shaped members 15 and 16, which can be manufactured at low cost, need to be replaced.

Next, the action will be explained. The spring constant of the disc spring 12 is determined by appropriately selecting the ratio h/t of its plate thickness t and free height h (in this embodiment, h/t
= Indicates a case within the range of 1.2 to 1.5. ), the characteristics shown by the dotted line in FIG. 9 can be obtained. That is, by bending the disc spring 12 in advance by the dimension of the free height h and elastically deforming it into a flat plate shape, the spring constant m of the disc spring 12 in this area becomes extremely small, and the spring constant m in this area becomes very small. As a boundary, the spring constant m of the disc spring 12 changes non-linearly in either direction of the amount of deflection. At this time, the load n applied to the disc spring 12 has a characteristic as shown by the solid line in the figure, and as the amount of deflection of the disc spring 12 increases, the rate of increase in the load decreases, and the amount of deflection is free. When the height becomes equal to h, the rate of increase in the load becomes zero, and when the amount of deflection is further increased beyond this point P, the load increases non-linearly.

On the other hand, the disc spring 12 and the ring-shaped members 15,1
Although the hardness of No. 6 is significantly harder than other structural members such as the spring receiving member 11, the difference in hardness between the two members is set to be small. Therefore, even if the disc spring 12 is elastically deformed under the load that fluctuates in the vertical direction due to vibration input from a vehicle, etc., and the diameters of the inner and outer peripheral edges 12a and 12b change, the disc spring 12 has a large hardness. Since the spring 12 and the ring-shaped members 15, 16 directly rub against each other, there is no possibility of galling between the disc spring 12 and the ring-shaped members 15, 16. Therefore, the lower spring receiving portion 10
There is no need to provide a special device for lubricating the lower spring receiving portion 10, and galling of the lower spring receiving portion 10 can be reliably prevented with a simple structure.

If the disc spring 12 is elastically deformed by the free height h in advance, it will be set at a point P where the rate of increase in the load becomes zero, so the spring of the disc spring 12 in this state will be The constant will be extremely small. Therefore, the coil spring 1 and the lower spring receiving portion 10 are elastically connected while ensuring a certain amount of load transmission force (enough to support the weight of the vehicle). Therefore, vibrations are input from the road wheel side or the vehicle body side and are transmitted to the coil spring 1 or the lower spring receiving part 10, but high-frequency vibrations with a relatively small amplitude that are not attenuated by the coil spring 1 are , it is absorbed and attenuated by the disc spring 12, which has a small spring constant when set.

Figure 10 compares the vibration characteristics q of a conventional support device consisting of a single coil spring 1 and the vibration characteristics r of a support device according to the present invention that uses a disc spring 12 in combination with the coil spring 1 in terms of vibration transmission force. It is something. As shown in the figure, according to the present invention, it is possible to suppress the vibration input due to the surging phenomenon from being transmitted to the vehicle body, thereby improving the quietness in the vehicle interior.

Note that the disc spring 12 may be provided on both sides of the coil spring 1, and the disc spring 12 may have a shape such as a diaphragm spring used in a clutch device, which has a radially extending slit on the inner edge side. It may have a shape like this. In this case, the amount of deflection of the disc spring can be set larger than in the case of the above embodiment.

As explained above, in the present invention, in a spring support device in which a coil spring is interposed between a support body and a supported body, and the support body is supported by the support body, the support body or the supported body A disc spring having a spring constant that is elastically deformed into a flat elastic disk shape by being bent by a dimension of the free height under a load when the vehicle is stationary is interposed between at least one of the coil spring and the coil spring, and further, The space between the inside of the disc spring and the supporting body or the supported body, and between the outside of the disc spring and the supporting body or the supported body have a hardness close to that of a disc spring and are in line contact with the disc spring. A ring-shaped member is interposed to provide a structure in which the load is received on the inside and outside of the disc spring. Therefore, it is possible to elastically connect the supporting body or the supported body and the coil spring by reducing the spring constant while ensuring a certain degree of load transmission force, and it is also possible to connect the coil spring to the supporting body or the supported body and the coil spring with a small spring constant. A ring-shaped member with high hardness can be brought into direct contact.
Therefore, it is possible to suppress vibration input due to the surging phenomenon that occurs in the coil spring when vibration is input from being transmitted to the vehicle body, reducing noise inside the vehicle interior and improving its quietness. At the same time, it is possible to prevent galling between the disc spring and the member on the supporting body side or the member on the supported body side. Furthermore, it is possible to provide a structure for preventing galling of disc springs that does not require a special lubricating device or the like to prevent galling, has a simple structure, and can be manufactured at low cost.

[Brief explanation of the drawing]

FIG. 1 is a front view showing a conventional spring support device for a vehicle, FIG. 2 is a front view showing a spring support device for a vehicle as a prior art, and FIGS.
The figure shows one embodiment of the present invention.
The figure is a front view showing the entire device, FIG. 4A is a front view of a spring receiving member which is a component of the present invention, FIG. 4B is a central vertical sectional view of FIG. 6 is a central longitudinal sectional view of the member, FIG. 7 is a central longitudinal sectional view of the ring-shaped member, and FIG. 8 is a central longitudinal sectional view of the disc spring receiving member. Figure 9 is a spring characteristic diagram of a disc spring, 10th
The figure is a diagram showing the relationship between vibration frequency and transmitted force. 1...Coil spring, 3...Strut tube, 7...Atsupa spring seat, 8...
Mounting insulator, 9...Vehicle side plate, 10...Lower spring receiving part, 1
1... Spring receiving member, 11a... Spring seat,
11b... Spring seat, 11c... Ring groove,
12... disc spring, 12a... outer periphery, 12b...
Inner peripheral edge, 13... Disc spring receiving member, 13a... Spring seat, 13b... Ring groove, 15, 16... Ring shaped member.

Claims (1)

[Claims] 1. In a spring support device in which a coil spring is interposed between a support body and a supported body, and the supported body is supported by the support body, at least either the support body or the supported body and the coil spring On one side, a disc spring having a spring constant that is elastically deformed into a flat elastic disk shape by bending by the free height dimension under the load when the vehicle is stationary is interposed, and further, the inside of this disc spring and the support or between the supported body and between the outside of the disc spring and the supporting body or the supported body,
For a vehicle, each of the ring-shaped members has a hardness close to that of a disc spring and has a shape that makes line contact with the disc spring, so that the load is received on the inside and outside of the disc spring. Spring support device.