JPS5940031A - Vehicular spring supporting device - Google Patents

Abstract

PURPOSE:To minimize the fluctuation of the spring constant of a belleville spring and at the same time reduce the wear at the engaging part of the belleville spring in the device, in which the belleville spring is interposed at least either between a supporting body and a coiled spring or between a body to be supported and the coiled spring. CONSTITUTION:A belleville spring 12 is interposed between a spring seat, onto which the coiled spring is seated, and a belleville spring retaining member 13, which is fittingly fixed onto a strut tube 3. The inner peripheral edge of the belleville spring 12 is supported through a ring-shape member 16 by the retaining member 13. A sealing member 17 consists of an inside lip ring 18, the diameter of which is a little smaller than that of the ring-shape member 16, and an outside lip ring 19, the diameter of which is a little larger than that of the ring- shape member 16. Lubricant to reduce the wear of the engaging part of the belleville spring with the ring-shape member 16 is packed in the space of the sealing member 17. In addition, the lubrication at the engaging part makes the frictional force smaller at all times, resulting in maintaining the hysteresis of the belleville spring smaller and enabling to prevent the fluctuation of the spring constant of the belleville spring from generating.

Description

[Detailed description of the invention] The present invention relates to a spring support device for a vehicle.

As a conventional spring support device 6 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-tube shock absorber, is removably attached to the strut tube B. Built-in. A piston (not shown) is loosely fitted into the cylinder tube, and the piston (not shown) divides the inside of the cylinder into a clay chamber and a royal chamber, and the lower end of a piston rod 40 whose upper end protrudes outside the cylinder tube is fixed to this piston. be. and,
The lower end of the strut tube B is fixed to the steering knuckle 5 or the like.

Further, numeral 6 in the figure is a lower spring seat, and this lower spring seat 6 is externally fitted onto the slide/lat duplex 6 and fixed by welding. and,
The coil spring 1 is compressed between an upper spring seat (not shown) fixedly fixed to the upper part of the piston rod 4, either directly or via a rubber sheet or the like. Furthermore, there is a circular knot (not shown) on the upper spring seat of Pimeton Totsudo 4. ! A mounting in/unit (shown in the figure) is interposed between the outer cylinder (not shown) fixed to the vehicle body 1111 with a bolt nut and the inner cylinder.

The upper end of the shock absorber to which the coil spring 1 is attached is connected to the vehicle body side, which is a supported body, and the lower end of the shock absorber is connected to the road wheel side, which is a support body.

However, in such a conventional spring support structure for a vehicle, the lower spring seat 6 of the support body 11111 or the upper spring seat on the supported body side and the coil spring 1 are in self-contact contact, or It had a structure in which it was attached to the shell through a sheet, etc. Therefore, not only when the upper spring seat 6 of the lower spring seat 6 and the coil spring 1 are in face-to-face contact, but also when the two are brought into contact via a rubber sheet, etc., the rubber sheet, etc. is the spring of the coil spring 1. It is compressed by force and becomes hard, and the actual removal is done through a rubber sheet with extremely hardness, etc. d Mi, in contact with i body weight. Therefore, when the frequency of the vibration input from the support body measurement or the supported body side matches the fixed frequency of the coil spring 1, the two-one spring 1 resonates, and this causes the coil spring A coarse portion and a dense portion are formed in one stretching direction, and these portions move in the same direction, causing a so-called surging phenomenon. As a result,
Unreasonable force acts locally on the coil spring 1, which not only impairs riding 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, this applicant previously filed an application for a spring support device having a structure as shown in FIG.
No. 21.80, Title of Invention: Spring Support Device for Vehicles). The spring support device shown in FIG. 2 has a coil spring 1 interposed between a support body and a supported body, and the support body is supported by the support body. A plate d and a spring 12 are provided between the support body or the supported body and the coil spring 1.
is interposed, and furthermore, the inside and outside of this disc spring 12 (I1
Ring-shaped members 15 and 16 are interposed between each side of 1+ and the supporting body and the supported body.

That is, as shown in Fig. 3 after being disassembled into parts 1 (A) to (3), the spring receiver forms a spring seat 11b on the upper surface of the member 11, which has a necessarily spiral shape on which one end of the coil spring 1 is seated. At the same time, an outer spring seat 11a into which the outer peripheral edge 12a of the disc spring 12 is fitted is formed on the lower a1, and an outer spring seat 11a is formed in the outer 1H11 spring (↑11a is provided with a ring groove 11c that continues in the circumferential direction. The ring-shaped member 15 on the outer circumferential side is inserted into this ring groove 11c.In addition, on the upper surface of the disk spring receiving portion 13 (supported body), there is an inner spring on which the inner circumferential edge 12b of the disk spring 12 is fitted. A ring groove 13b continuous in the circumferential direction is provided in this inner spring seat 13a, and an inner ring-shaped member 16 is inserted into this ring groove 13b. The receiver fixes the member 13 to the outside of the strut tube 3 , and brings the lower surface of the inner peripheral edge of the disc spring 12 into contact with the inner ring-shaped member 16 . The disc spring 12 is interposed between the spring receiver member 11 and the disc spring receiver member 13.! so that the members 15 are in contact with each other.

At this time, 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 non-linear, so that low frequency vibrations with a relatively large amplitude can be generated. When the vibration is inputted, the vibration is inputted directly to the coil spring 1 via the disc spring 12 which is largely elastically deformed and has a large spring constant, thereby reducing the vibration. The small high frequency vibrations are absorbed and attenuated by the disc spring 12 having a small spring constant when set.

In the figure, 10 is a part of the lower flink receiver, the spring receiver is composed of a member 11 and a disc spring 12, and the disc spring receiver, which is a supported body, is composed of a member 16 i<fL. In addition, 7 is a supporting body (upper spring seat), 8 is a fd mounting insulator, 9 is a crawling vehicle body side plate, and 14 is a
This is a nut for tightening the upper end of the car body (fl, i + plate 9υ5 screws) and rod 4.

1 to 2, however, the prior art vehicle spring support device VC shown in FIG. j6
in direct contact with and applied to the contact area with,
For example, with an excretory lubricant such as grease, HH(t=lJ i'
: 112 and the ring-shaped members 15 and 16 are structured to provide lubrication. . For this reason, the lubricant flows out from the contact portion in a short period of time, and as a result, the frictional force between the disc spring 12 and the ring-shaped member 15° 16 increases, and the frictional force between the disc spring 12 (1 - There was an insufficient point that the J hysteresis became large and the spring constant did not change in actual operation, but the contact part between the disc spring 12 and the ring-shaped member 15 and 16 was accelerated to wear out. .

The present invention was made in view of the inadequacies of the prior art, and provides a spring support device in which a coil spring is interposed between a support body and a supported body.
A disc spring is interposed between at least one of the support body or the supported body and the coil spring. A ring-shaped member is interposed therebetween, and a sealing member is interposed between the disk spring and the multi-supported body or the supported body so as to surround the ring-shaped member, and the portion surrounded by the sole member By filling a coffin 1 lubricant to lubricate the part where the countersunk plate and the ring-shaped member contact,
The purpose of this invention is to maintain the lubricant in a predetermined position for a long period of time to ensure lubricity between the disc spring and the ring-shaped member, thereby solving the above-mentioned inadequacies.

In the following, the present invention will be explained based on the drawings.

FIG. 4 and FIG. 5 Q show essential parts of an embodiment of the present invention, and the lower flywheel 31 bearing of the strut type front suspension in which a coil spring and a shock absorber are provided on the same axis is part 100. FIG. 2 is an exploded view and a cross-sectional explanatory view of main parts.

1. First, to explain the configuration, the lower spring receiver is part 1.
0, as shown in exploded view in FIGS. 4(4) to (4), a disc spring 12, a sealing member 17 on the inner peripheral side, a ring-shaped member 16 on the inner peripheral side, and a disc which is a supported body. The spring holder consists of a member 13, and the sprinkle holder (not shown) arranged above the disk spring 12 consists of a part, seal members on the outer periphery side, and a ring-shaped member on the outer periphery side, all of which are ring-shaped. to do.

The Im spring 12 shown in FIG. The free height of the spring 12 is h. Then, this plate d
It is preferable that the spring 12 is set to have a free height equal to its plate thickness t, and furthermore, the spring force of the disc spring 12 is
The amount of deflection of the spring 2 is set to be equal to the free height h due to the load received from the coil spring 1 when the vehicle is stationary, so that the spring 2 is elastically deformed into a flat Z-disk shape.

The seal portion 17 on the inner circumferential side shown in FIG. Unlike the lip ring 19, the inner lip ring 18 is formed so that its cross-sectional shape is concave inward in the radial direction, and the cross-sectional shape of the outer lip link 19 is opposite to that of the inner lip ring 18. It is formed so that it is concave outward in the radial direction. The material of the lip ring 18, 19 is made of an elastic material such as elastically deformable rubber or synthetic resin. The structure of the seal member on the outer circumferential side used above the countersunk spring 12 is the same as the structure of the seal member 17 on the inner circumferential side, so its description and illustration 1 will be omitted.

In this embodiment, the ring-shaped member 16 on the inner periphery side i (the same applies to the ring-shaped member on the outer periphery (not shown)) shown in FIG. One location in the direction is cut out to form a C-shape, and although it is preferable to form it in this way from the viewpoint of ease of assembly, it may be continuous in an endless manner. ! , the cross-sectional shape of this ring-shaped member 16 is other than square-c
4 = Rege circular shape (not limited to elliptical shape, etc., but its character is as follows. The book spring holder, which will be described later,
3b, the culm is so large that a part of it in the cross-sectional direction is exposed from the surface of the inner spring seat 13a.

The inner diameter of the B material 16 for the countersunk splash receiver shown in FIG. The inner circumferential edge 12b forms an externally fitted inner spring PJ15a, and the inner spring seat 13aK is further provided with a ring groove 13b continuous in the circumferential direction. And inner spring seat 13a @1
With the disc spring holder facing upward, the member 16 is fitted onto the strut tube 6 and fixed to the strut tube by welding.

The structure of the spring receiver 11 and other members is similar to that of the prior art shown in FIGS. 2 and 3.

To assemble this vehicle spring device, the spring receiver fixed in advance to the strut tube A is inserted into the ring groove 13b of the member 16, and the ring-shaped member 16 on the inner peripheral side is inserted. An inner lip ring 18 is arranged inside the ring-shaped member 16 with the concave side facing radially inward so as to be surrounded by the sealing member 17, and an inner lip ring 18 is disposed on the outside of the ring-shaped member 16 with the concave side facing radially inward. The outer lip ring 19 is arranged facing outward. Thereafter, the four-fold portion 20 of the seal member 17 is filled with a lubricant such as grease.

Next, with the concave surface facing upward, insert the inner peripheral edge 12b of the disc spring 12.
The disc spring receiver is loosely fitted and seated on the inner spring seat 13a of the part 16, and the outer spring seat 11a of the member 11 is loosely fitted to the outer peripheral edge of the disc spring 12. At this time, the spring receiver is placed in the ring groove 11c of the member 11.
In addition to inserting the ring-shaped member 15 on the outer circumferential side in advance, a sealing member on the outer circumferential side is arranged so as to surround this ring-shaped member 15, and a lubricant such as grease is applied to the area surrounded by the sealing member. By filling and applying the lubricant, the sealing member is adhesively supported on the spring receiver member 11 side by the viscosity of the lubricant. After that, this spring retainer becomes part vJ1.
The lower end of the coil spring 1 is seated on the spring seat 11b of the coil spring 1, and the upper end of the coil spring 1 is covered with the upper spring seat 7. Furthermore, from above the upper spring seat 7, the mounting insulator 8 and the vehicle body side plate 9 are attached to the piston. Fits onto the top of the rod 4. The coil spring 1 is held in a predetermined compressed state by the tightening of the nut 14 that is screwed into the male thread on the upper part of the piston rod 4, and the upper spring seat 7, the mounting insulator 8, and the vehicle body.
Tighten and fix the rib plate 9.

In this way, the upper end of the shock pump bar equipped with the coil spring 1 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 serving as a support.

In addition, the hardness HD of the disc spring 12 and the ring-shaped member 15°1
The relationship between 6 and hardness H8 is Rockwell hardness, IH8
-HD It is preferable to set it so that 1≦10, and in particular, Hs (
It is best to set it to HD. In this case, since the disc spring 12 is harder than the ring-shaped member 15.16, the ring-shaped member 15.16 will wear out more quickly, and the ring-shaped member 15.16 can only be replaced because it can be manufactured at low cost. That's enough.

In addition, in the embodiment described above, the inner and outer peripheral edges 12 of the disk spring 12
Ring-shaped members 15 and 16 are in contact with the sides of a and 12b.
However, the circumferential length of the outer ring-shaped member 150 is longer than the circumferential length of the inner circumference (11i IJ ring-shaped part 16), and its stress is significantly greater than that of the inner ring-shaped part 16. Because of its low height, the use of the outer ring-shaped member 15 is omitted and the disc spring 1 is
The ring-shaped member 16 may be interposed only on the inner circumferential side of 2.

Further, the disc springs 12 may be provided on both sides of the coil spring 10, and the shape of the disc springs 12 is such that a diaphragm spring used in a clutch device is provided with slits extending radially on the inner edge side. It may also be shaped 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. Furthermore, the edges of the inner and outer peripheral edges 12a and 12b of the disc spring 12 may be in contact with the ring-shaped members 15 and 16.

Next, the effect will be explained.

Due to the input of vibrations from wheels etc., the disc spring 12 is elastically deformed under the load that fluctuates in the vertical direction.
Even if the diameters of the outer peripheral edges 12a, 12b change, since the disk spring 12, which has a hardness, and the ring-shaped member 15.16 directly rub against each other, the gap between the disk spring 12 and the ring-shaped portion control 5.16 is reduced. There will be no 9-year hiatus. The ring-shaped members 15 and 16 may be surrounded by a ring member 17, and the portion surrounded by this seal member 17 is filled with a lubricant such as IJ-glue. Therefore, the parts where the leaf spring 12 and the ring-shaped member 15, 16 are in contact are always lubricated with lubricant, so that the disc spring 12 and the ring-shaped member 15
．． 16 can be kept small at all times. Therefore, since the hysteresis of the disc spring 12 can be kept small, a substantial change in the spring constant can be prevented. Furthermore, the lubricant is applied to the sealing member 1
7 and does not flow out from the area surrounded by the seal member 17, it is possible to ensure the lubrication of the contact area for a long period of time, and to greatly suppress wear of the contact area. can do.

Other embodiments of the invention are shown in FIGS. 6-9.

The embodiment shown in FIGS. 6(G) and 6(B) is a ring-shaped member 1
6, a seal member 17 is fixed by baking. That is, an inner lip ring 18 and an outer lip ring 19 that are continuous along the ring-shaped member 16 are baked on the inner circumference (full + and outer circumference side) of the ring-shaped member 16, respectively, and the ring-shaped member 16 and the sealing member 17 are bonded together. With this structure, the sealing member 170 and the ring-shaped member 16 can be assembled at the same time, and the number of man-hours required for introduction can be limited.

In the embodiment shown in FIGS. 7(G) and 7(B), the inner lip ring 18 and the outer lip ring 19 are continuous to form the sealing member 17, and the continuous portion of the sealing member 17 is The spring receiver is in the ring groove 13 of the member 13. b
The sealing member 17 is configured to be inserted into the ring-shaped member 16 and fixed.

In the embodiment shown in FIGS. 8(4) and 8(B), the countersunk ball bearing is attached to the inner (1111
The 1J tube ring 18 and the outer lip ring 19 are baked and fixed, and the disc spring holder is attached to the member 16.
and a seal member 17 are integrally constructed.

119 (5), (B) II (In the illustrated embodiment, an inner lip ring 1 is attached to the side surface of the inner peripheral edge of the disc spring 12.
8 and the outer lip ring 19 are baked and fixed, thereby integrally forming the disc spring 12 and the seal portion t417. Note that 21 is a sealing member on the outer peripheral side. In the embodiments shown in FIGS. 6 to 9, since the sealing member 17 is integrally constructed with the outer members such as the ring-shaped member 16, it is easy to assemble. The adhesion properties can be greatly improved.

As described above, the present invention provides a spring support device in which a coil spring is interposed between a support and a supported body, and the supported body is supported by the support. A disc spring is interposed between at least one of the support body and the coil spring, and further between at least an inner side surface or edge of the disc spring and the support body or the supported body. A ring-shaped member is interposed in the ring-shaped member, and a sealing member is interposed between the plate spring and the supporting body or the supported body so as to surround the ring-shaped member, and the ring-shaped member is surrounded by the sealing member. The portion is filled with a lubricant for lubricating the portion where the disc spring and the ring-shaped paulownia portion come into contact. For this reason,
The lubricant can be held at a predetermined position fe for a long period of time, and the lubricant can constantly keep the portion where the disc spring and the ring-shaped member are in contact with each other in smooth movement. therefore,
The frictional force between the disc spring and the ring-shaped member can be kept small at all times, the hysteresis of the disc spring can be kept small, and changes in the spring constant over the actual η can be prevented. can. Moreover, since the lubricant is retained by the seal and does not flow out from the area surrounded by the seal, it is possible to ensure lubricity between the disc spring and the ring-shaped member. , it is possible to obtain the effect that wear and tear on the contact portion between the disc spring and the link-like member can be significantly reduced.

[Brief explanation of the drawing]

Fig. 1 is a front view showing a conventional vehicle spring support chain, Fig. 2 is a front view showing a prior art spring support chain for both storage and storage, and Figs. 3(A) to 3 are shown in Fig. 2. The lower spring receiver is a cross-sectional view of the parts constituting the parts, and FIGS.
The figure is an explanatory view of the main parts of the lower spring receiver shown in Fig. 4, and Figs. 6 (4) and (B) are explanatory views of the main parts showing the second embodiment of the present invention. Figure (A), (
B) is a main part explanatory diagram showing the third embodiment of the present invention, No. 8
Figures (5) and (B) are clear views of the main part R'l showing the fourth embodiment of the present invention, and Figure 9 (5) and a3) are the fifth embodiment of the present invention.
1 (This is a diagram showing an example. 1... Coil spring, 6... Strut tube, 10... Lower spring holder is part, 11...
11a spring seat, 11b spring seat, 11c ring groove, 12 disc spring,
12a...outer circumference &', 12b...inner circumference H113...
The disc spring receiver is a member, 13a... Spring seat, 13b... Ring groove, 15.16... Ring-shaped member, 17... Seal member, 18.19... Lip ring, 20... Seal. Partial patent applicant enclosed in the old 17 Nissan Motor Co., Ltd. agent Patent attorney Tetsuya Mori Patent attorney Yoshiaki Naito Kiyoshi
Mizu, Attorney-at-Law, Masaru Kajiyama
Kore No. 7 ffflJ Broom 911 1

Claims (1)

[Claims] A coil spring is interposed between the support body and the supported body,
In a spring support vortex in which a supported body is supported by a support body, at least one of the support body or the forest support body and the coil spring,
A disc spring is interposed 2, and a ring-shaped member is interposed between the side surface or edge of the disc spring and the supporting body or the supported body, A sealing member is interposed between the disc spring and the supporting body or the supported body so as to surround the ring-shaped portion, and the sealing member is used to seal the disc spring and the ring in the quadruple area. 7. A spring support device for a vehicle, characterized in that the spring support device is filled with a lubricant for lubricating the portion that comes into contact with the shaped member.