KR830000486B1 - Shock absorber - Google Patents

Abstract

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Description

Shock absorber

1 is a cross-sectional view taken along line 1-1 of FIG. 2 of the piston and the cylinder of the shock absorber according to the present invention.

2 is a vertical cross-sectional view taken along the line 2-2 of FIG.

3 is a side view of a piston head having a split ring similar to the cylindrical casing shown in FIG. 2 in another embodiment according to the invention.

FIG. 4 is an enlarged detail view showing a method for preventing rotation of a ring associated with a piston head, as seen in the direction of arrow 4-4 of FIG.

5 and 6 are partial cross-sectional views showing another embodiment using a piston head with flange flange notches similar to that shown in FIG.

FIG. 7 is a cross-sectional view of a ring similar to that of FIG. 1 but having a pair of vertical grooves formed by two ring notches having a pair of opposite ends.

8 is a horizontal sectional view of a shock absorber having a floating adjustment component according to the present invention.

The present invention relates to a shock absorber, in particular a fluid exclusion shock absorber, which is also used in automobiles and supported by other devices or mechanisms to be used for cushioning or repelling shock. The piston for a hydraulic shock absorber of the above type has a valve which opens somewhat in proportion to the pressure difference between both sides of the piston head in an operation chamber built by the shock absorber casing.

The flow path controlled by this method is usually supplemented by the installation of an auxiliary passage where the valve is not opened or closed, wherein the auxiliary passage is generally referred to as a "permanent passage".

The permanent passage reduces the vibration of itself when the shock absorber is connected to the wheel spring suspension of the vehicle and serves to comfortably ride.

However, the cross section of the permanent passage should be comparable to the flow path of valve opening and closing when the piston is opened by the valve during reciprocation at a suitable speed.

It has been found that the shape of the permanent passage has a great influence on comfortable riding, and the thin slit that defines the passage can make itself more comfortable than the round hole.

In a permanent passage with round holes, the laminar flow is changed to abrupt turbulence, resulting in a change in discharge rate, which results in faster and more frequent turbulence than with thin slits with the same cross section.

However, the resistance to hydraulic fluid flow through the thin slit varies greatly depending on the viscosity of the hydraulic fluid used in the shock absorber. So the shock absorber with a permanent passage is actually formed of a thin slit-shaped piston that has the effect of reducing the temperature increase of the piston

In order to prevent a decrease in efficiency with rising temperature, the low viscosity oil suddenly changes the laminar flow into turbulent flow and selects a low viscosity hydraulic fluid without satisfactory effect.

Moreover, the decrease in efficiency due to the temperature factor is not completely improved even by the use of low viscosity oil, and the phenomenon affecting the existing shock absorber has a satisfactory result even by the permanent passage defined by the round hole. Can't get it.

The shock absorber according to the present invention is designed to allow complete correction of temperature even when using a thin slit-shaped permanent passage and oil having a relatively high viscosity.

The shock absorber according to the present invention prevents the generation of turbulence, which is necessary for the shock absorber to be most comfortable when used in connection with the wheel spring suspension of the vehicle.

A split ring with a high coefficient of expansion surrounds the piston head and is held at least in radial radial motion between the shock absorber casing and the piston head and at least in the vertical perpendicular motion between the ring and the piston head, at least in advance. It has a pair of opposing free ends that are spaced a fixed distance apart and are held in place by a radially expanding flange on the piston.

The groove having a rectangular cross section and a slit is defined by the space between the edge of the piston and the inner wall of the casing and the space between the opposite ends.

One or both of the flanges are arranged in the space between the opposing free ends of the ring.

A ring made of plastic and having a high coefficient of expansion will expand in length with increasing temperature, so that the opposite free end of the ring is closer, reducing the size of one of the passages.

In other words, the cross-sectional area of the groove is reduced.

The open ring, made of the same plastic material as the tape between the piston and the cylindrical casing of the shock absorber and containing fiberglass, is a Mac-Pherson type suspension crutch that is subjected to large lateral stresses of the piston against the cylindrical casing. strue).

The open ring is used for the purpose of providing improved piston-sliding capability and for the dual purpose for a more complete seal between the piston and the cylindrical casing.

The ends of the rings are joined in a specially designed shape and slit only to improve the provision of the housing to hold them in a fixed position.

In Patent No. 2,719,612, the application of which is already registered in the United States of America, a shock expander is a material that is sufficiently inflated to reduce the thickness of the thin plate-shaped passages installed in the piston to compensate for the damping reduction caused by the reduced viscosity of the oil. Explained to have an annular ring made of.

However, the present invention differs with respect to the prior art functions, operations and suspension supports.

In addition, the permanent passage of the rectangular cross section has been specifically addressed in the present invention, the cross section according to the above

The present invention does not use annular spaces or clearances, unlike the shock absorbers of US Pat. No. 2,719,612, which facilitate the passage of fluids on the side of one piston relative to the other piston.

In particular, only a shock absorber is shown for clarity in the various parts according to the present invention.

Thus, in FIG. 2, only a part of the cylindrical casing 10 extending in the axial direction is shown, which is characterized by the fact that a typical working chamber containing the hydraulic liquid L is built in.

The piston is installed to reciprocate in the operating chamber and includes a piston rod 11 and a piston head 12 connected by a nut 13.

The end of the piston rod 11 was extended out of the cylindrical casing 10, the piston rod 11 and the cylindrical casing 10 is appropriately installed in place to control the mutual movement between the buffer and the non-buffering agent. have. (Not shown)

The piston head 12 with the side wall 14 is generally a suitable metal material.

As shown in FIG. 2, the side wall 14 has a diameter smaller than the inner diameter of the casing, and the lower annular flange 16 and the upper annular flange 15 extend in the circumferential direction outward of the side wall, and the piston It lies on both sides 17 and 18 of the head 12.

The split ring 19 of suitable thickness surrounds the side wall of the piston head 12, although not the power supply, and is held so as not to be moved in the axial direction by the flanges 15 and 16 on both sides.

The flange can move in a very fine axial direction of about 0.1 mm between the ring and the piston head 12.

In addition, the outer diameter of the ring is about 0.1 mm smaller than the inner diameter of the casing to allow movement in the circumferential direction between the ring and the casing.

The circumferential and axial movements promote friction prevention which enables flexible reciprocation of the pistons.

Thus, the above very small circumferential motion is in the form of an annular space in the form of a permanent passage in which fluid flowing from one side of the piston passes in the form of a thin film or sheet, as in US Pat. No. 2,719,612. It does not limit the gap.

The ring 19 has a coefficient of expansion larger than the material of the piston head 12. Thus, the material of the ring is, for example, a fluororesin, acetal resin, polyamide, teflon, darylpin, nylon and the like.

The rings with opposing free ends 21 and 22 are positioned at a predetermined distance D, for example 5-10 mm. (Figure 1)

The ring therefore does not completely surround the side wall of the piston head. The space between the free ends 21 and 22 and the space between the respective portions 10a and 14a (FIG. 1) of the casing side wall determine the groove 23 having a rectangular cross section, and the groove The shape of is equal to the difference between the inner radius (R) of the casing and the outer radius (C) of the side wall of the piston, and the distance (D), that is, the clearance equal to the distance between both sides (17) (18) of the piston head. Is the shape of.

Lower flange 16 has notches 24 that fit snugly with the space between ends 21 and 22 (FIG. 6

In other cases, as in FIG. 2, the upper flange 15 of the groove 23a defines a notch and only the lower flange 16 has a notch.

The width of the groove 23a is defined as the difference between the outer diameter r of the upper flange (less than the radius) and the outer diameter C of the piston head side wall.

The groove 23b also defines that there is no notch in the lower flange 16 as shown in FIG.

The upper and lower flanges are different in diameter, so that the width of the grooves 23b is appropriately adjusted.

According to the above, the groove defines a permanent passage for the control of the hydraulic liquid moving between both sides of the piston head in which the piston reciprocates. However, the size of the grooves decreases due to an increase in temperature which causes the length of the split ring 19 to increase.

The rings of opposing free ends 21 and 22 are brought closer together by the reduction of the distance D of the thin slit due to the increase in temperature, and consequently the cross sectional area is reduced.

The slit distance formed as described above is suitably selected as a function of the expansion coefficient, and the proper design of the piston valve (described later) allows perfect temperature correction for changes in oil viscosity at all piston reciprocating speeds.

The grooves designed in accordance with the present invention are designed to achieve a temperature-independent damping effect such that the flow of hydraulic fluid is diameterd by the cutting of the flanges 15 and 16 of FIG. 6 or as shown in FIG.

It is also possible to only notch the upper flange instead of the lower flange. One or the other, or both, flanges axially arranged and notched in the space between the free ends 21, 22 should be able to prevent rotation of the split ring 19 relative to the piston head.

A small stud or pin 26 may be provided for this purpose, which pin is mounted to the piston head so that the side wall meets in a properly provided groove in the dividing ring 19 (first and second degrees). Extends toward the bar.

It is also possible to prevent rotation about the piston head by providing projections 27 and 28 (FIG. 4) which extend from the ring at the free end and are supported for each side of the notch 24.

Of course, the protrusion must be able to withstand the side of the notch 25 sufficiently.

As shown in FIG. 3, the free ends 21, 22 of the ring must be inclined at the corner 29 to adjust the passage of hydraulic fluid through the groove 23.

And the opposing free ends 21, 22 of the ring should be parallel to each other in the axial direction of the piston and, if desired, parallel to each other at an angle (not shown) in the axial direction.

Although only one groove has been described, several grooves can be made without departing from the scope of the present invention.

For example, as in FIG. 7, the ring is in the same manner as described in the groove 23, with another pair of opposed pairs positioned apart at a predetermined distance D to define another groove.

A pair of ring segments 19a and 19a may be installed for this purpose.

And pins 26a and 26a are installed to prevent rotation of the ring section relative to the piston head in the same manner as described with reference to pin 27.

The groove 23 defined by the distance D 'is also characterized by the notch of the flange, not just the flange, or just one flange notch as described above.

FIG. 8 shows a drawing of U.S. Patent No. 3,844,389 already filed by Applicant who described a hydraulic shock absorber with a floating control valve.

The specification of Patent No. 3,844,389 is incorporated herein by reference in its entirety.

The structure of the piston is the same as that of the patent except that the permanent passage is installed in the valve 31 as described in US Pat. No. 3,844,389.

Instead, the permanent flow passage is defined by the groove 23 in the same way as the above described figure.

And the lateral passage 32 is connected to the notch 33 of the central washer 34 is installed in the piston head.

The notch is closed by a bearing washer 35 which is usually supported by a retaining disc 36.

The various notches 33 installed have the function of irradiating for the shock absorber, which determines the portion of the passageway provided to the fluid when the inner edge of the valve 31 begins to rise.

The function and operation of the notch 33 as a valve is described in detail in the above-mentioned US Pat. No. 3,844,389.

It may be used according to various temperatures with a slight change in description without departing from the scope of the invention.

Claims (1)

It has a cylindrical casing (10) surrounding the operating chamber with hydraulic fluid (L), the piston can reciprocate in the operating chamber, the piston is a cylinder connected to the piston rod (11) and the rod It has a piston head 12, the hydraulic fluid L is used between both sides of the piston head 12 during the reciprocating motion, the non-metallic split ring 19 is the side wall 14 of the piston head ), The cylindrical casing (10) has an inner diameter and the split ring (19) has an outer diameter slightly smaller than the inner diameter of the cylindrical casing (10), both sides of the piston head (12) The annular flange 15, 16 at the side extends straight to the side wall 14, allowing only the split ring 19 to be connected laterally while the piston head 12 is reciprocating. To both sides of the ring And the flanges 15 and 16 have an inner diameter slightly smaller than the inner diameter, and the dividing rings 19 are connected and are not integral and separated by a predetermined distance D. And at least one pair of opposed free ends 21, 22, wherein the space between the free ends 21, 22 and the side wall 14 and the inner wall of the cylindrical casing 10 are defined by the piston. Defining at least one groove 23 for adjusting the damping effect during the reciprocating motion, and the space between the free ends 21, 22 varies according to the change in temperature of the split ring 19 A hydraulic shock absorber characterized by varying the size of 23 and adjusting the damping effect.

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