KR980010019A - Hydraulic shock absorber adjusting damping force - Google Patents

Abstract

An object of the present invention is to broaden the adjustment range of the damping force characteristic and obtain an ideal damping force characteristic in the damping force adjustment type rest time cushion. The piston 2 is inserted into the cylinder 1 and the reservoir 5 is connected. The thrust disc valves 17 and 16 are worn on the elongated side 24 and the shrinking side passages 31 and the elongated side back pressure chamber 30 and the shrink side back pressure chambers 30 and 37 are provided on the back side thereof . The extension side back pressure chamber 30 is communicated with the cylinder upper and lower chambers 1a and 1b via the fixed orifice 38 and the sub disc valve 27 and the ports 47 and 45. [ Side back pressure chamber 37 is communicated with the lower cylinder chamber Ib and the reservoir 5 through the fixed orifice 39 and the sub disc valve 34 and the ports 42 and 47. [ The shutters 43 change the passage areas of the ports 40, 45, 42 and 47 so as to adjust the characteristics before the main disc valves 12 and 16 are opened and at the same time the elongation side back pressure chamber 28 / The internal pressure of the valve 33 is changed to adjust the characteristics after the valve is opened. The valve characteristics are obtained before opening the main disc valves 12 and 16 with the sub disc valves 27 and 34. [

Description

Hydraulic shock absorber adjusting damping force

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view showing a damper-force-regulating hydraulic buffer according to a first embodiment of the present invention; Fig.

2 is a longitudinal sectional view of a damping force generating mechanism which is a main part of a second embodiment of the present invention

3 is a longitudinal sectional view of a damping force generating mechanism which is a main part of a third embodiment of the present invention.

4 is a longitudinal sectional view of a damping force generating mechanism which is a main part of the fourth embodiment of the present invention.

5 is a view showing a damping force adjusting type hydraulic shock absorber according to a fifth embodiment of the present invention.

5 is an exploded perspective view of the jaw disk valve of the apparatus of FIG.

7 is a perspective view of the plate spring of the apparatus of FIG.

8 is a view showing a reduction force characteristic of the damping force adjusting type hydraulic buffer according to the present invention,

Fig. 7 is a longitudinal sectional view of a damping force generating mechanism which is a main part of a sixth embodiment of the present invention. Fig.

10 is a longitudinal sectional view of a damping force generating mechanism which is a main part of a seventh embodiment of the present invention

11 is a plan view of a retainer under the floating valve of the apparatus of Fig.

Figure 12 is a perspective view of the floating valve of the apparatus of Figure 10;

DESCRIPTION OF THE REFERENCE NUMERALS

1 cylinder 3: piston rod

2 'Piston 5: reservoir

12: Disk valve (extension side main damping valve)

16: disk valve (shrink-side main damping valve) 24: elongated passage

27: sub disc valve (elongation side damping valve) 30: elongation side back pressure chamber

31: Shrinkage side passage 34: Sub-disc valve (shrinkage side damping valve)

37: retraction side back pressure chamber 38: fixed orifice (upstream side passage on the extension side)

39: Fixed orifice (water side upstream passage)

40: Guide port (variable-side variable orifice)

41: Guide port (downstream side passage on the extension side)

45 Shutter port (variable side orifice)

46: Shutter port (downstream side passage on the extension side)

42: Guide port (variable orifice on the contraction side, downstream passage)

47: Shutter port (shrinkage-side variable orifice, downstream passage)

[TECHNICAL FIELD OF THE INVENTION AND RELATED ART OF THE SAME]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a damping force adjusting type hydraulic shock absorber mounted on a suspension device such as an automatic lowering device. A hydraulic shock absorber mounted on a low suspension device such as an automatic loader has a damping force adjustment type hydraulic shock absorber that can adjust the damping force appropriately in order to improve the maneuverability and steering stability according to the road surface situation and driving situation.

Generally, a damping force-regulating hydraulic shock absorber divides a piston into seven chambers by inserting a piston connected with a piston rod into a cylinder in which oil is sealed, A damping force generating mechanism including an orifice and a disk valve is provided in the main oil passage and a damping force adjusting valve is provided in the bypass passage for adjusting the passage area thereof . In addition, one chamber (?) In the cylinder is connected through a reservoir base valve that compensates for a change in the volume of the cylinder due to expansion and contraction of the piston rod by compression and expansion of the gas.

The damping force is adjusted by reducing the flow resistance of the oil between two chambers in the cylinder by opening the bypass passage by the damping force adjusting valve. In addition, by increasing the damping force by increasing the flow resistance of the seven passages by closing the bypass passage have. As described above, the damping force characteristic can be appropriately adjusted by opening and closing the damping force adjusting valve. But. As described above, the damping force is adjusted by the passage area of the bypass passage because the damping force depends on the orifice characteristic of the oil passage in the low speed region of the piston speed, Since the sensing power depends on the damping force generating mechanism (disk valve, etc.) of the main oil passage, there is no significant change in the specific strength.

Therefore, conventionally, as described in, for example, Utility Model Publication No. 72-155242, a pressure chamber is formed in a portion of a disk valve that is a mechanism for generating a force in a main oil passage provided in a piston portion, Is communicated with the cylinder chamber on the upstream side of the disc valve through the variable orifice and communicated with the cylinder chamber on the downstream side of the disc valve through the variable orifice.

According to this damping force adjusting type hydraulic buffer, by opening and closing the variable orifice, the opening area of the two chambers in the cylinder can be adjusted and the initial pressure of the opening of the disk valve can be changed by changing the pressure in the pressure chamber. Thus, the orifice characteristic and the valve characteristic can be adjusted, and the adjustment range of the damping force characteristic can be widened.

[Technical Problem]

However, the damping force-regulating hydraulic shock absorber provided with the judging force generating mechanism and the damping force adjusting valve in the above-mentioned conventional piston has the following problems. When the flow resistance of the piston portion increases with respect to the base valve that is opened (opened) between the cylinder chamber and the reservoir, the outflow of the oil to the reservoir becomes excessive due to the contraction stroke, The stable damping force can not be obtained. like this. Since the damping force characteristic on the contraction side depends on the flow resistance of the base valve, the adjustment range of the damping force characteristic on the contraction side is narrowed.

8, the damping force before the opening of the low speed region side disc valve of the piston speed is determined by the variable area of the variable orifice orifice and there is a characteristic of being squared with respect to the piston speed. Therefore, when the passage area of the variable orifice and the fixed orifice is set so as to obtain a proper damping force in the braking region of the piston speed, sufficient damping force can not be obtained in the extremely low speed region. On the other hand, when the passage area of the variable orifice and the fixed orifice is set so as to obtain a sufficient damping force in the extremely low speed region, the damping force becomes too large in the low speed region near the opening point 8 of the disc valve. As described above, there is a limitation in the adjustment range of the damping force characteristic, and there is a problem that the damping force characteristic that can be sufficiently satisfied can not be obtained.

Further, since the damping force generating mechanism is provided in the piston portion, the stroke of the piston rod becomes shorter as the piston portion increases. Further, since the normal damping force adjusting valve is operated through the operating rod inserted through the piston rod, the design freedom of the shape of the attachment portion of the piston rod on the lower body side is restricted.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a damping-force-regulated hydraulic shock absorber which can broaden the adjustment range of the damping force characteristic and obtain the ideal damping force characteristic in the high-speed region and the low-

[Structure and operation of the invention]

In order to solve the above problems, a damping force type hydraulic damper according to claim 1 is characterized in that a damping force type hydraulic damper according to claim 1 has a cylinder having an oil filled therein, a piston slidably inserted in the cylinder and partitioning the inside of the cylinder into two cylinder chambers and one end connected to the piston And a piston connected to the cylinder, the other end extending to the outside of the cylinder to compensate for a change in the volume of the cylinder due to expansion and contraction of the piston rod by compression and expansion of the gas, A shrinkage-side passage for circulating oil from one cylinder chamber to the other cylinder chamber during an extension stroke of the piston rod, an extension-side main damping valve for adjusting a passage area of the extension-side passage, Side back pressure chamber in which an internal pressure acts in the direction of the closing valve, Side main damping valve and a cylinder chamber on the upstream side of the elongation-side main damping valve and a valve opening pressure lower than the elongation-side main damping valve to adjust the passage area of the elongated- A downstream side passage for communicating the downstream side back pressure chamber and the cylinder chamber on the downstream side of the downstream side main damping valve with a subordinate damping valve, a variable side orifice for adjusting a passage area of the downstream side downstream passage, Side back-pressure chamber for applying an internal pressure in the direction of the closing valve to the valve body of the main-damping valve on the contraction side, and a valve seat on the upstream side of the shrinkage-side main damping valve A valve is opened with a contraction-side upstream passage communicating with the cylinder chamber and an opening valve pressure lower than the contraction-side main damping valve A downstream side passage for communicating the contraction side backpressure chamber and the downstream side of the contraction side damping valve and a downstream side passage for communicating the upstream side passage and the contraction side downstream passage, And a shrinkage-side variable orifice to be adjusted.

In addition to the above, the damping force adjusting type hydraulic shock absorber according to claim 2, wherein the extension side and the shrinkage side main damping valve are provided with a valve force spring installed to move back and forth with respect to the valve seat and a laminated leaf spring for pushing the valve body toward the valve seat side And the elongated side lower shrinkage side damping valve is an eccentric disc valve having an orifice passage.

The damping force adjusting type hydraulic shock absorber according to claim 3 is characterized in that, in addition to the configuration of claim 2, the leaf spring is disk-shaped, and the outer diameter of the leaf spring and the disk valve is the same.

The damping force adjusting type hydraulic shock absorber according to claim 4 is characterized in that, in addition to the configuration of claim 2 or 3, a valve element is provided between the valve body and the valve seat so as to open and close the valve seat.

The damping force adjusting type hydraulic shock absorber according to claim 5 is characterized in that, in addition to the configuration of claim 4, the valve member is supported by the valve body.

According to the adjustment type hydraulic buffer according to claim 1, when the piston rod is extended, the oil flows between the two cylinder chambers through the extension side passage, the extension side upstream passage, the extension side back pressure chamber and the extension side downstream passage, A damping force is generated by the elongated side damping valve, the elongated side variable orifice and the elongated side main damping valve, and the damping force characteristic by the elongated side damping valve before the elongated side main damping valve is opened by changing the passage area of the elongated side variable orifice The opening pressure of the elongation side damping valve and the damping force characteristic after opening can be changed by varying the internal pressure of the elongation side back pressure chamber while the elongation side main damping valve and the valve opening The valve characteristics can be obtained before. In the contraction stroke, the oil flows from the cylinder chamber to the reservoir through the shrinkage-side passage, the shrinkage-side upper passage, the shrinkage-side back pressure chamber, and the shrinkage-side downstream passage, and the shrinkage side damping valve, the shrinkage- The damping force is generated by the main damping valve and the passage area of the variable orifice on the contraction side is changed to directly change the damping force characteristic by the contraction side damping valve before opening the main damping valve on the contraction side, The opening pressure of the contraction-side damping valve and the damping force characteristic after the opening can be changed. At this time, the valve characteristic can be obtained before the contraction-side main damping valve is opened by the contraction- In addition, since the flow of oil between the cylinder chamber and the storage chamber is controlled to spark the damping force at the time of the compression stroke, the negative pressure is not generated in the cylinder chamber due to the flow resistance of the variable orifice and the damping valve, and stable damping force can be obtained.

The damping force control type hydraulic shock absorber according to claim 2, in addition to the above, has a laminated structure of the leaf spring light disc valve, so that the vibration is attenuated by the friction between the laminated members.

According to the damping force adjusting hydraulic lancet of claim 3, in addition to the above, it becomes more common to use the pipe spring and the dis- closed valve.

By improving the flexible valve member in addition to the above according to the precision force-regulating hydraulic buffer according to the fourth aspect of the present invention, the sealability between the valve body and the valve seat during the cowling valve is improved.

According to the damping force-regulating hydraulic buffer of claim 5, in addition to the above, since the valve member follows the valve body, the close contact between the valve body and the valve seat and the valve member of the closing valve is improved.

[Example]

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The damping force generating mechanism shown in Figs. 1 to 4 shows the state at the time of the extension stroke on the right side toward the ground, and the state on the left side in the contraction stroke.

The first embodiment will also be described with reference to Fig. 1, the damping-force-regulating hydraulic buffer according to the first embodiment is structured such that a piston 7 is slidably inserted in a cylinder 1 sealed with oil, and the piston 1 is connected to the cylinder 1 ) Is partitioned into two cylinder chambers of a cylinder upper chamber la and a cylinder lower chamber Ib. One end of the piston rod 3 is dented in the piston 2 and the other end of the piston rod 3 is inserted into a guide seal 4 mounted on the end of the cylinder 1, It is a series. A reservoir 5 in which oil and gas are sealed is provided in the outer periphery of the cylinder 1 and communicates with the cylinder lower chamber Ib through a base valve 6 provided at the bottom of the cylinder 1. [

The piston 2 is provided with a check valve 7 which permits only the oil to flow from the chamber side Ib to the cylinder side chamber 1 A check valve 8 is provided which permits only the oil to flow from the lower cylinder chamber Ib side to the cylinder lower chamber Ib side.

In addition, a judging force generating mechanism 9 is provided outside the cylinder 1.

The damping force generating mechanism 9 has an annular valve member 11 fitted in order from the lower side in a substantially cylindrical case 10 having a bottom portion and a main disc valve 12, 13 and the housing 14 are superimposed on each other and the annular tumbler member 15 is fitted and the main disc valve 16, the spacer 17 and the housing 18 are laid thereunder. They are integrally fixed by penetrating a generally cylindrical guide member 19 having a bottom portion inserted from the bottom side into the case 10 and screwing the nut 20 to the tip end portion.

The inside of the case 10 is partitioned into three oil chambers 10a, 177, and 10c by valve members 11 and 15. [ The case 10 is provided with a flow passage 21 for communicating the oil chamber 10a with the cylinder upper chamber 1a, a flow passage 22 for communicating the oil chamber 17b with the lower chamber Ib, And a flow path 73 for communicating the reservoir 5 is provided.

The valve member 11 is provided with an elongated passage for communicating the oil chamber 10a and the oil chamber 10b, that is, the cylinder upper and lower chambers la and Ib through the hu- midity 21 and the oil passage 22, (24) are provided. An annular valve seat 25 is provided so as to protrude from the outer peripheral side of the opening of the elongated passage 24 on the end face of the valve member 11 on the oil chamber 10b side, A main disc valve 12 is provided as a main attenuation valve. The main disc valve 12 receives the oil and pressure on the side of the oil chamber 10a of the elongated passage 24 and opens on the outer circumferential side to allow the oil to flow to the oil chamber 10b side, Thereby generating a damping force.

The valve member 11 is provided with an annular valve seat 75 protruding between the opening of the elongated passage 74 and the valve seat 75 with a projecting amount smaller than that of the valve seat 25, And a sub disc valve 27 as an extension side damping valve is provided on the upstream side of the disc valve 12 so as to face the valve seat 26. [ A notch (not shown) is provided in the sub disc valve 27 to form an orifice passage that allows the passage of the elongated passage 24 at all times. Further, the sub-disc valve 27 is formed by stacking a plurality of (two shown) disc-shaped members, and receives the pressure on the oil chamber 10a side of the elongated passage 24, The malleus is open and is designed to generate a damping force according to its opening degree. Or the disc valve 27 opens the valve at a pressure lower than that of the main disc valve 12.

An annular sealing member 78, one end of which is in contact with the main disc valve 12 in a liquid tight manner, is slidably fitted in the opening of the housing 14 formed into a layer shape having a bottom. The sealing member 28 is always in contact with the main disc valve 17 by the spring 29 and is urged by the housing 14 and the sealing member 28 to the downstream side of the main disc valve 12 Side back pressure chamber 30 is formed.

The valve member 15 is provided with a shrinking-side passage for communicating the oil chamber 10b with the oil chamber 10c, that is, the cylinder lower chamber Ib and the reservoir 5 through the oil passage 22 and the oil passage 73, (Long) is installed. An annular valve seat 32 is provided so as to protrude from the outer peripheral side of the opening of the retraction side passage in the oil chamber 10c of the valve member 15, The main damping valve chuck main disc valve 16 is installed. The main disc valve 16 receives the pressure of the oil on the side of the oil chamber 10b of the shrinkage side passage 31 and the outer peripheral side is bent so that the valve is opened to allow the oil to flow toward the oil chamber 10c, So as to generate a damping force.

The valve member 15 is provided with an annular valve seat 33 protruding between the opening force of the retraction side passage 31 and the valve seat 37 so as to protrude from the valve seat 32 smaller than the valve seat 32, And a sub disc valve 34 as a contraction side side damping valve is provided on the upstream side of the disc valve 16 so as to face the valve seat 33. The sub-disc valve 34 is provided with a notch (not shown) and an orifice passage for allowing the contraction-side passage 31 to always flow. Further, the sub-disc valve 34 is formed by stacking a plurality of (seven as shown) disc-shaped members, and receives the pressure of the oil chamber 10b side of the contraction side passage 31, The valve is opened, and a damping force is generated in accordance with the degree of opening. In addition, the sub-disc valve 34 is opened to a pressure lower than that of the main disc valve 16.

An annular sealing member 35 whose one end is in liquid-tight contact with the main disc valve 16 is slidably fitted in the opening of the housing 18 formed into a cylindrical shape having a bottom. The sealing member 35 is always in contact with the main disc valve 16 by the spring 36 and is urged by the housing 18 and the sealing member 35 on the downstream side of the main disc valve 16 Side back pressure chamber 37 is formed in the back-pressure side back pressure chamber 37.

The main disc valve 12 is provided with a stationary orifice as an extension side upstream passage which communicates the extension side back pressure chamber 30 with the oil chamber 10a, that is, the side of the cylinder upper chamber 1a via the sub disc valve 27, And the shrinkage back pressure chamber 37 is connected to the main disc valve 17 via a clutch of the sub disc valve 34 so as to communicate with the oil chamber 10b side, Side orifice 39 as a downstream-side upstream passage.

The side wall of the guide member 17 is provided with a guide port 40 communicating with the extension side back pressure chamber 30, a guide port 41 communicating with the oil chamber 10b and a guide port 41 communicating with the contraction side back pressure chamber 37. [ (42) are provided.

A cylindrical shutter 43 is rotatably fitted in the guide member 19. An operation rod 44 is connected to the shutter 43 and one end of the operation rod 44 is extended to the outside so that the shutter 43 can be rotated from the outside by the operation rod 44. On the side wall of the shutter 43, shutter ports 45, 46, and 47 are provided so as to face the guide ports 40, 41, and 47, respectively.

The shutter port 45 and the shutter port 46 are in communication with each other through a shutter chamber 43a formed in the shutter 43. The shutter chamber 43a, the shutter boats 45, , 41 constitute a downstream passage of the extension side back pressure chamber (30). The shutter port 47 and the guide port 47 constitute a downstream passage of the build-up side back pressure chamber 37 and communicate with the oil chamber 10Oc through the opening of the guide member 19. [

And. A variable orifice is formed in the guide port 40 and the shutter port 47 and a variable orifice on the contraction side is formed in the guide port 42 and the shutter port 47. By the rotation of the shutter 43, So that the area of the communication path of the fuel cell can be freely changed. The guide port 41 and the shutter port 45 are always communicated with a constant passage area irrespective of the rotational position of the shutter 43. [

The operation of the first embodiment constructed as described above will be described as follows.

When the piston rod 3 is extended, the check valve 7 is closed by the movement of the piston 2 to pressurize the oil on the cylinder-side chamber la side and the oil chamber 10a, The back pressure chamber 30, the guide port 40, the shutter port 45, the shutter chamber 43a, the shutters 43a, the shutters 43a, 43b of the sub-disc valve 27, the stationary orifice 3B, Flows through the port 46, the guide port 41, the oil chamber 10b, and the oil passage 27 to the cylinder lower chamber Ib side. When the pressure on the cylinder side chamber la reaches the opening pressure of the main disc valve 12, the main disc valve 12 is opened and the oil flows directly from the extension side passage 24 to the oil chamber 10b . On the other hand, the oil of the rod withdrawal rune in the cylinder 1 due to the extension of the piston rod 3 is supplied from the reservoir 5 to the cylinder lower chamber Ib via the check valve 8 by the expansion of the gas do.

A damping force is generated in accordance with the passage area of the variable side orifice of the extension port formed by the guide port 40 and the shutter port 42 before the main disk valve 19 having a small piston speed is opened. At this time, in the extremely low speed region of the piston speed, a damping force of the orifice characteristic is generated by the orifice formed by the notch portion of the sub disc valve 27. When the piston speed is increased, the disc valve 27 is opened, Therefore, the damping force of the valve characteristic becomes serious. Further, the piston speed increases and the pressure on the side of the cylinder-side chamber 1a rises, and the damping force of the valve characteristic is generated in accordance with the degree of opening of the main risk valve 12.

Therefore, as shown by the solid line in FIG. 8, the damping force characteristic becomes the orifice characteristic by the notch portion of the sub disc valve 77 up to the valve opening point A of the sub disc valve 27, The valve characteristic according to the degree of opening of the disc valve 27 becomes a valve characteristic according to the opening degree of the main disc valve 12 after the change point B of the main disc valve 12. [ By forming the bending point (change point A) in the damping force characteristic of the low speed region by means of the sub disc valve 27 in this way, the damping force in the low speed region can be adequately attained and the thrust force in the extremely low speed region can be sufficiently secured.

The shutter 43 is rotated from the outside by the operation rod 44 to adjust the damping force characteristic by changing the communication path area of the variable orifice (the guide port 40 and the shutter port 45) on the extension side . At this time, since the pressure loss becomes larger as the communication passage area of the variable orifice on the extension side becomes smaller, the pressure in the upstream side back pressure chamber 30 becomes higher and the pressure in the oil chamber 10a And the pressing force in the direction of the closing valve of the main disc bulb 12 is increased, so that the opening degree of the main disc valve 17 is increased. Further, the larger the communicating path area of the elongated variable orifice, the lower the pressure in the elongation side back pressure chamber 30, and the lower the pressure of the oil chamber 10a on the upstream side of the main disc valve 17, The opening valve pressure of the valve 12 is lowered.

Therefore, since the damping force characteristics before and after opening of the main disc valve 12 are simultaneously changed by rotating the shutter 43 and changing the passage area of the variable side orifice, the change in the damping force And the adjustment range of the damping force characteristic can be widened.

During the contraction stroke, the check valve 7 is opened by the movement of the piston 2, so that the oil in the cylinder lower chamber Ib directly flows into the cylinder upper chamber la, And Ib are equal to each other and the flow of oil does not occur between the flow path 21 of the damping force generating mechanism 9 and the flow path 22. [

On the other hand, the check valve of the base valve 6 is closed and the oil as much as the introduced oil of the rod entering the cylinder 1 along with the short axis of the piston chord 3 is pressed to the side of the cylinder lower chamber Ib, 22, the oil chamber 10b, the shrinkage side passage (Keen), the cutout portion of the abutment valve 34, the fixed orifice (steam), the shrinkage side back pressure chamber 37, the guide port 4f, When the pressure in the cylinder 1 reaches the opening pressure of the pressure disc valve 16, the pressure in the main disc valve 16 17 are opened so that the oil flows directly from the contraction side passage 31 to the oil chamber 1OC.

Before the opening of the main despatch valve 16 having a small piston speed, a characteristic decreasing force is generated in accordance with the passage area of the variable-side orifice on the contraction side composed of the guide port 42 and the pot port 47. At this time, in the extremely low speed region of the piston speed, a damping force of the orifice characteristic is generated by the misalignment formed by the cutout portion of the sub disc valve 34, and the disc valve (gun) is opened when the piston speed is increased. A valve characteristic and a damping force according to the degree of opening are generated. Further, when the piston lattice becomes large and the pressure of the cylinder upper and lower chambers la and Ib rises and the main disc valve 16 is opened, a damping force of the valve characteristic is generated in accordance with the opening degree.

Therefore, as shown by the solid line in FIG. 8, the orifice characteristic is formed by the notch portion of the sub disc valve 34 up to the valve opening point A of the sub-desk valve 27 The valve opening point B of the main disc valve 16 is determined by the degree of opening of the main disc valve 16, Valve characteristics. Thus, by forming the bending point (change point A) with the damping force characteristic of the low speed region by the sub disc valve (run), the damping force in the low speed region can be adequately attained and the damping force in the extremely low-

The damping force characteristic can be adjusted by changing the passage area of the variable orifice by rotating the shutter 47 from the outside by the operation rod 44. [ At this time, as in the case of the extension stroke, the pressure in the contraction side back pressure chamber 37 changes in accordance with the communication path area of the variable-side orifice on the contraction side, and the opening valve pressure of the main disc valve 16 changes. Therefore, by varying the passage area of the variable orifice on the contraction side by rotating the shutter 43, the damping force characteristics before and after opening of the main disc valve 16 change simultaneously, so that the change in the damping force And the adjustment range of the damping force characteristic can be widened.

When the shutter 43 rotates, the variable side orifice formed of the guide port 40 and the shutter port 45 and the communication passage area of the variable side orifice of the shrinkage side comprising the guide port 42 and the shutter port 47 The damping force characteristic independent of the extension side and the contraction side can be obtained.

In this case, for example, depending on the rotational position of the shutter, when the passage area of the variable orifice on the extension side or the shrinkage side is one side (clothes), the other side is small (7 ·) (For example, a combination of an extension-side hardness, a shrinkage-side softness, a elongation-side softness and a shrinkage-side hardness) of a kind of damping force characteristics different from each other in size on the extension side and the shrinkage side by providing the guide ports and the cartridge- Can be set. Further, at the time of the contraction stroke, the shrinkage-side variable orifice (guide port 47, shutter port 47) provided between the flow path 22 communicating with the cylinder lower chamber Ib and the flow path 23 communicating with the reservoir 5 47). And the flow resistance of the main disc valve 16 is generated by the flow resistance of the sub disc valve (long) and the main disc valve 16. Since the flow resistance is not acted between the upper and lower chambers la and Ib, The inside of the cylinder 1 does not become a negative pressure, so that a stable damping force can be obtained. Further, the setting range of the damping force characteristic can be widened.

Next, a second embodiment of the present invention will be described with reference to Fig. The second embodiment is substantially the same as the first embodiment except that the structure of the shutter of the damping force generating mechanism is different from that of the first embodiment. Will be described in detail.

As shown in Fig. 7, in the light damping force generating mechanism 65 according to the second embodiment, a spool 66 is slidably inserted in the guide member 19 instead of a rotary shutter.

A guide port 67 is provided on the side wall of the guide member 19 to communicate with the oil chamber 10c. The guide ports 40 and 41 are communicated with each other through the flow path 68 of the spool 6 so that a variable side orifice is formed. 67 so that the contraction-side variable orifice is formed. By the movement of the spool 66, the area of each communication passage can be freely changed.

A compression spring 70 is provided at one end of the spool 66 and an actuating rod 71 of an actuator is brought into contact with the other end of the spool 66. The spool 66 is rotated by the actuator against the elastic force of the spring 70, Is adjusted to adjust the passage area of the variable orifices on the extension side and the contraction side. Reference numeral 77 in the figure is a passage for introducing pressurized oil into the oil chamber 10c at the other end side of the spool 66 to balance the pressure acting on both ends of the bubble 66. [

With this configuration, as in the first embodiment, before the main disc valves 17 and 16 are opened, damping is caused by the sub disc valves 27 and 34, and the spool 66 is moved by the actuator, The damping force characteristics before the opening of the main disc valves 12 and 16 on the extension side and the contraction side are adjusted and the pressure of the expansion side back pressure chambers 30 and 37 is changed It is possible to adjust the damping force characteristics after the main disc valves 12 and 16 are opened.

Next, a third embodiment of the present invention will be described with reference to FIG. 3. In the third embodiment, since the spool of the damping force generating mechanism is moved by the pilot pressure, the third embodiment has almost the same structure except that the spool of the damping force generating mechanism is moved by the pilot pressure. Therefore, Explain only the fire and other details.

3, in the damping force generating mechanism 73 according to the third embodiment, the pile spin 74 and the pressure control valve 75 are provided on one end side of the spool 66 in the guide member 19 have. Further, a pilot passage (orifice) 76 for communicating the pilot chamber 74 and the oil chamber 10a is provided.

The pressure control valve 75 is provided in the relief chamber 78 communicating with the pylon chamber 74 through the communication passage 77 so that the needle nee seal 79 can move back and forth and the needle 79 And relieves the pressure oil in the pilot chamber 74 that has reached the predetermined pressure to the relief chamber 78. The needle 79 is connected to the plunger of the proportional s- And the relief pressure of the pressure control valve 75 can be freely adjusted in accordance with the energizing current to the solenoid. The relief chamber 78 is connected to the passage 72 To the oil chamber 10c.

With this configuration, during the extension stroke, the pressurized oil on the side of the cylinder chamber la pressed by the movement of the piston 2 is introduced from the oil chamber 10a through the pilot passage 76 into the pile concealment chamber 74. Then, the spool 66 is moved to a position where the pressure of the oil (pilot pressure) in the pilot chamber 74 is balanced with the pressing force of the spring 70, and the passage area of the variable orifice is adjusted. At this time, when the pilot pressure reaches the luer vacuum pressure of the pressure control valve (Class 7), the needle 79 retracts and the pressure oil in the pilot chamber 74 is relieved to the relief chamber 78, The displacement of the spool can be controlled by adjusting the pilot pressure.

As in the seventh embodiment, a damping force is generated by the sub-disc valve 77 before opening the main disc valve 17 on the extension side, and further, by the movement of the spool 67, And the damping force characteristic after opening of the main disc valves 12 and 16 can be adjusted by varying the pressure of the elongation side back pressure chamber 30. On the other hand, at the time of the contraction stroke, the piston horses 3, The upper and lower chambers 1a and 1b are pressed together as the cylinder 1 is introduced into the cylinder li so that the internal pressure of the cylinder 1 is introduced from the oil chamber 10a to the pilot chamber 74 through the pilot passage 76. [ In the same way as during the extension stroke, the damping force is generated by the sub disc valve 34 before opening the main disc valve 16 on the contraction side, and furthermore, by the energizing current of the solenoid, The damping force characteristic before the main disc valve 17 and opening And adjusts the damping force special after the opening of the main disc valve 17 by changing the pressure of the back side pressure chamber 37. The fourth embodiment of the present invention will be described with reference to FIG. The fourth embodiment is substantially the same as the first embodiment except that the auxiliary valve is provided on the downstream side of the variable orifice communicating with the back pressure chamber of the damping force generating mechanism. The same parts as in the embodiment are denoted by the same reference numerals and only the other parts are described in detail.

4, the damping force generating mechanism 50 according to the embodiment 714 is provided with the auxiliary valve member 81 between the housing 14 in the case 10 and the valve member IS, 18, the auxiliary valve member 82 is superimposed.

The auxiliary valve member 81 is provided with passages B and 7 communicating with the guide port 41. The auxiliary disk valve 84 and the orifice 84a are provided on the side of the belt seat and the orifice a4a has a smaller passage area than the fixed orifice 3B of the main disk valve 12. [

A guide port 55 is added to the guide member 19 so that the guide port 85 communicates with the oil chamber 10c through the passage 85 of the auxiliary valve member (reel). The guide port 85 is always in communication with the shutter port 77 added to the shutter 43 and communicates with the shutter port 47 through the shutter chamber 43b formed internally of the shutter 43 . The auxiliary valve member 87 is provided with the auxiliary disc valve 35 and the orifice 88a and the orifice Baa has a smaller passage area than the fixed orifice 37 of the main disc valve 16. [

Here, the auxiliary disk valves 84 and 83 serve to prevent the deterioration of the damping force characteristic caused by the change in viscosity of the oil (difficulty in blurring, difficulty in fogging) with temperature change. That is, when the temperature of the oil is low (when the viscosity of the oil is high), the auxiliary disc valves 84, 88 are opened, and the oil becomes easy to flow. In addition, when the temperature of the oil is high (when the viscosity of the oil is low), the auxiliary disc valve 84.88 is closed and the oil becomes difficult to fog.

With this configuration, the oil introduced into the shutter chamber 43a through the guide port 40 and the shutter port 45 (variable orifice) during the extension stroke passes through the shutter port 46, the guide port 41, And flows through the passage 83 of the member 81 to the oil chamber 10b. Thus, prior to the opening of the main 1.1 scoop valve 12, In the extremely low speed region of the piston speed, the damping force is generated by the notch and the orifice 84 of the sub disc valve 27, and when the piston speed is increased, the auxiliary disc valve 84 ) Opens the valve in a downward direction to generate a damping force.

Further, when the piston speed is increased and the main disc valve 12 is opened. A damping force is generated according to the degree of opening.

And. It is possible to directly adjust the damping force characteristic of the opening of the main disc valve IB by changing the passage area of the guide port 40 and the shutter port 45 (variable orifice) by rotating the shutter 43 as in the first embodiment At the same time, the damping force characteristic after the main disc valve If is opened can be adjusted by changing the pressure of the elongation side back pressure chamber 30.

At this time, since the pressure of the elongation side back pressure chamber 30 depends on the valve pressure characteristic (flow resistance) of the auxiliary disk valve 84, the pressure in the back pressure chamber is controlled only by the variable orifice, It is difficult to be influenced by the change in the viscosity of the oil caused by the oil, so that a stable damping force can be generated. In addition. When the pressure in the mixing chamber is controlled only by the variable orifice, the flow resistance of the variable orifice due to the decrease in the viscosity of the oil at the kinetic temperature is large, so that the opening valve pressure of the main disc valve 12 is lowered, .

The oil that has flowed into the shutter chamber 43b through the guide port 42 and the shutter port 47 (variable orifice) flows through the shutter port 87, the guide port 85, and the auxiliary valve member 82 Through the passage 86 of the oil chamber 10c.

Thereby, in the extremely low speed region of the piston speed before opening of the main disc valve 16, a decreasing force is generated by the notch portion and the orifice 88a of the sub disc valve 34. When the piston speed becomes large, Depending on the disc valve 34 and the viscosity of the oil, the auxiliary disc valve (bubble) opens the valve in a downward direction to generate a damping force. When the piston speed is increased and the main disc valve 16 is opened, a damping force is generated according to the opening degree.

By varying the passage area of the guide port 42 and the shutter port 47 (variable orifice) by rotating the shutter 43 as in the first embodiment, the damping force characteristic before the opening of the main disc valve 16 can be directly The damping force characteristic after the opening of the main disc valve 16 can be adjusted by changing the pressure of the contraction side back pressure chamber 37. [

At this time, since the pressure of the contraction side back pressure chamber 37 depends on the valve characteristic of the auxiliary disc valve 84, the damping force which is not influenced by the temperature and can be stably generated can be generated.

Next, a fifth embodiment of the present invention will be described with reference to Fig. 5 in Fig. Since the fifth embodiment has the same structure as that of the first embodiment (the more detailed structure is shown in Fig. 5) for the hydraulic shock absorbing basic body portion, the following description will be given for the portions corresponding to those of the first embodiment Describe it by number.

5, in the damping force generating type hydraulic shock absorber according to the fifth embodiment, the damping force generating mechanism 100 includes two valve members 102 and 103 fitted in the case 101 of the bottom cylinder, The proportional solenoid actuator 104 (hereinafter referred to as the actuator 104) is screwed into the opening through the retainer 104a and the inside of the case 101 is opened by the valve members 102 and 103, And is divided into chambers 101a, 101b, and 101c.

The valve members 102 and 103 are formed by inserting a substantially cylindrical guide member 107 through the annular fixing members 105 and 106 and screwing the leading end of the guide member 107 to the actuator 104, . The three oil chambers 101a, 101b and 101c are respectively connected to the cylinder upper chamber IA, the lower cylinder chamber Ib and the storage chamber 5, respectively.

The valve member 102 is provided with an elongated passage 108 for communicating the oil chamber 101a and the oil chamber 101b. An annular valve seat 109 is provided so as to protrude from the outer circumferential side of the opening of the elongated passage 108 in the valve member 102. An annular valve 109 having a larger protruding amount than the valve seat 107 is provided on the outer circumferential side thereof. A sheet 110 is provided so as to protrude. The valve seat 179 is fitted with a sub disc valve 111 which is an extension side damping valve. As shown in FIG. 6, the sub-disc valve 111 is formed by laminating a plurality of (four in all shown) discs olla and lllb, The valve is bent to open the valve due to the pressure of the oil to generate the damping force according to the opening degree. A notch lllc is formed in the outer periphery of the disk llmb in the valve seat 109 to form an orifice passage that allows the passage of the elongate passage 108 at all times.

A cylindrical sealing member 117 is slidably fitted to the outer peripheral portion of the fixing member 105. One end of the sealing member 112 is attached to the valve seat 110 of the valve member 107 and the outer peripheral portion of the disk-shaped tube spring 113 is tightly contacted with the flange portion formed inside the one end, That is, toward the valve seat 110 side. The sealing member 112 and the leaf spring 113 constitute an extension side main damping valve that receives the pressure of the oil on the oil chamber 101a side of the elongated passage 108 and opens to generate a damping force in accordance with the opening degree. . In addition, the opening valve pressure of the sub disc valve 111 is set to be lower than the opening valve pressure of the main side damping valve.

Also. The extension side back pressure chamber 114 is formed by the fixing member 105, the sealing member 112, and the leaf spring 113.

7, the plate spring 113 is formed by laminating a plurality of (four in all shown) disks 113a, l3b, and has the same outer diameter as the disk valve 111, The outer circumferential force of the disc l13b which contacts the flange portion of the bottom end bearing member 112 forms a fixed orifice for lifting the elongated side back pressure chamber 114 to the elongated side passageway 108 through the force dissipation valve 111 And a notched surface 113c is formed.

The valve member 103 is provided with a shrinkage-side passage 115 for communicating the oil chamber 101 and the oil chamber 101c. The valve member 10 is provided with an annular valve seat 117 protruding from the outer peripheral side of the opening of the shrinking side passage 117. The annular valve seat 117 is provided with a ring- And a valve seat 117 is provided so as to protrude from the valve seat 116. The sub disc valve 118 is attached to the valve seat 116. The sub disc 118 is, And the discs 118a and 118b are folded in one direction to receive the pressure of the oil on the oil chamber 101b side of the raking side passageway 115 and to unfold and open to generate a damping force corresponding to the opening degree have.

A notch 118c is formed in the outer periphery of the disc 118b to be placed on the valve seat 117 to form an orifice passage that allows the contraction passage 115 to be always allowed to flow.

The outer peripheral body of the fixing member 105 is slidably fitted with the sealing member 117 of the cylindrical cap. The outer peripheral portion of the circular tubular spring 120 comes into close contact with the flange portion of the sealing member 117 formed on the valve seat 117 of the valve member 103 and formed on the inner side of the one end so as to seal the valve seat 117 in the valve opening direction, 117). The sealing member 119 and the leaf spring 120 receive the oil pressure on the oil chamber 101b side of the spiral passage 115,

Side main damping valve is opened to generate a damping force according to the opening degree. The opening pressure of the sub disc valve 118 is set to be lower than the opening pressure of the main shunt-side damping valve.

The shrinkage-side back pressure chamber 121 is formed by the fixing member 105, the sealing member 119, and the leaf spring 120.

The tube spring 120 is formed by laminating a plurality of (four in all shown) disks 120a and 127b as shown in FIG. 7, as described above. The outer circumferential portion of the disk Ifob contacting the flange portion of the sealing member 119 is provided with a cutout portion 121 for forming a fixed orifice for communicating the contraction side back pressure chamber 121 with the contraction side passage 115 via the sub- 120c are formed.

The extension side back pressure chamber 114 communicates with the oil chamber 101b side via guide ports 122 and 123 (variable side orifice) provided on the side wall of the guide member 107. The back side pressure chamber Is communicated with the oil chamber 101c side through guide ports 174 and 125 (variable orifice on the contraction side) provided on the side wall of the guide member 107. [ A guide rib 177 is slidably inserted into the guide member 177 to adjust the communication area between the guide ports 177 and 173 and the guide ports 124 and 125 as in the second embodiment shown in FIG. have

The spool 126 is always urged to one side by the spring 177 so that the guide ports 122 and 123 can be rotated by the operation rod 128 of the actuator 104 against the urging force of the spring 177, And the communicating path areas between the guide ports 124 and 125 can be respectively adjusted.

The operation of the fifth embodiment constructed as described above will be described as follows. 5, the flow of oil during the extension stroke is indicated by a solid line arrow toward the left side of the drawing of the damping force generating mechanism 100 of FIG. 5, and the flow of oil at the contraction stroke is indicated by a broken line arrow to the right.

During the extension stroke of the piston rod 3, the check valve 7 is closed by the movement of the piston 2 so that the oil on the cylinder upper chamber 1a side is pressurized. As shown by a solid line arrow in FIG. 5, Flows into the oil chamber 101a of the damping force generating mechanism 100 through the oil passage 21, And the oil passage 101b and the oil passage 101b and the oil passages 103a and 103b are connected to the oil passage 101a and the oil passage 101b, When the pressure on the side of the cylinder bore chamber la reaches the opening valve pressure and the sealing member 112 which is the braking side main damping valve is opened, the force disc valve 111 The oil as much as the piston rod 3 is extended and retracted from the cylinder 1 is expanded by the expansion of the gas in the storage chamber 5, (8) is opened and supplied to the cylinder lower chamber (Ib).

The damping force is generated in accordance with the area (variable orifice area) formed between the guide ports IB2 and 123 between the guide ports IB2 and 123 before the valve of the sealant material 112 (extension side main damping valve) opens. At this time, in the extremely low speed region of the piston speed, a damping force of the orifice characteristic is generated by the orifice passage formed by the cutout lIIC of the sub disc valve 111. When the piston speed becomes large, the sub disc valve 111 opens, A damping force of the valve characteristic is generated according to the degree of opening. When the piston speed is increased and the pressure of the cylinder-side chamber 1a rises and the sealing member 112 is opened, a sensing power of the valve characteristic is generated according to the opening degree.

During the contraction stroke, the check valve 7 is opened by the movement of the piston 2, so that the oil in the lower cylinder chamber Ib flows directly into the upper chamber la of the cylinder. And Ib are at the same pressure and no oil flows between the flow path 21 and the flow path 2f of the damping force generating mechanism 100. [

On the other hand, the check valve B of the face valve 6 is closed and the oil of the rod intrusion ring into the cylinder 1 along the short axis of the piston rod 3 is pressed. As shown by the dotted arrows Side passage 115, the sub-disc valve 118, the cut-out portion 127c of the leaf spring 120, and the oil chamber 101b through the hood 22 from the cylinder lower chamber Ib, And flows to the storage chamber 5 side through the contraction side back pressure chamber 171, the guide ports 174 and 175, the oil chamber 101c and the oil passage 73. [ When the pressure in the cylinder upper and lower chambers la and Ib reaches the opening valve pressure and the sealing member 119 serving as the shrinkage side main damping valve is opened, the oil is supplied to the oil chamber 101b through the sub disc valve 118, Lt; / RTI >

Before the opening of the sealing member 11! 1 (main damping valve on the contraction side), the piston speed is small and the damping force is glowing in accordance with the communicating passage area (the area of the variable orifice) between the guide ports 124, 125. At this time, in the extremely low speed region of the piston speed, a damping force of the orifice characteristic is generated by the orifice passage formed by the cutout portion 118c of the sub disc valve 118. When the piston speed becomes large, When the pressure of the lower chambers la and Ib rises and the sealing member 119 opens, a damping force of the valve characteristic is generated in accordance with the degree of opening.

Therefore, the damping force is generated by the sub disc valves 111 and 120 before the sealing members 112 and 119, which are the main damping valves on the extension side shrinkage side, are opened. Further, as in the third embodiment, 104 to move the spool 135 to adjust the communication path area between the guide ports 122, 173 which are the variable orifices on the extension side and the shrinkage side and the guide ports 124, 125, The damping force characteristics before opening of the sealing members 117 and 119 are adjusted and the damping force characteristics after the opening and opening of the sealing members 112 and 119 on the membranes are changed by modifying the pressure in the extension side back pressure chambers 114 and 121

Depending on the position of the spool 126, when the passage area of the variable orifice on the extension side and the contraction side is large, one of the two is small, and the other is small when one is small. (For example, a combination of an extension-side hardness and a shrinkage-side softness, or a combination of a softness-side shrinkage-side hardness) and a combination of damping force characteristics of different kinds of sizes on the extension side and the shrinkage side by providing the respective guide ports and the shutter port have.

Further, as in the other embodiments described above, when the piston rod 3 is contracted, the flow resistance does not act between the upper and lower chambers la1b, so that the negative pressure does not occur in the upper chamber la A stable damping force can be obtained, and the setting range of the damping force characteristic can be widened.

Since the sub disc valves 111 and 118 and leaf springs 113 and 120 have a structure in which a plurality of discs are stacked, vibration is damped by friction between the discs, Can be reduced. The discs 111a and 111b constituting the force disc valves 111 and 113 and the discs 11a and 11b 118a and 118b constituting the leaf springs 113 and 170 have the same diameter, It is possible to reduce the manufacturing cost, which can vacate them by obtaining the desired flexibility by the silkworms.

Next, a sixth embodiment of the present invention will be described with reference to Figs. 9 and 11. Fig. The sixth embodiment is substantially the same as the fifth embodiment except for the structure of the extension side of the damping force adjusting mechanism and the structure of the main damping valve on the contraction side. Hereinafter, the same portions as those of the seventh embodiment will be denoted by the same reference numerals and only different portions will be described in detail.

7, in the damping force generating mechanism 130 of the hydraulic shock absorber, the damping force adjustment according to the seventh embodiment is different from the damping force generating mechanism 130 of the hydraulic shock absorber in that the sealing member 11Ift 119 and the burn sheet 110. 111 of the valve members 102, A floating valve 131, 132 as a valve member is stored. The floating valve (long) 13f is a tapered annular member and is slidably fitted on the outer periphery of a cylindrical retainer (one lock) 134 fixed to the guide member 107. The one end face is sealed by the sealing members 118 and 119, 117a of the valve members 10f, 103 to contact the annular surface formed on the sealing member 112 and the sealing portions 112a, 119a of the valve member 10f, And is sealed.

As shown in FIG. A plurality of protruding portions 131a and 132a are formed in the inner circumferential portion of the blotting valve 137. The protruding portions 133a and 134a of the protruding portions 131a and 132a are inserted into the retaining portions 133 and 134, And is guided so as to be slidable in accordance with the moving direction of the sealing members 112 and 117. Floating valves (1, 132) Passages 135, 136 are formed between the retainers 133, 134. The fixed orifices (cutting forces 113c and 120c) of the leaf springs 113 and 170 are communicated with the extension side and the side of the contraction side passages 108 and 115 through the passages 135 and 137, respectively. The diameters of the sealing portions 117a and 117a of the sealing members 112 and 119 are smaller than the diameters of the valve sheets 110 and 117 of the valve member 107 and 103.

With this configuration, The seventh embodiment of the present invention achieves the same operation and effect.

Since the floating valves 131 and 137 having flexibility between the sealing members 117 and 119 and the valve sheets 110 and 117 are opened substantially in the form of a rigid body, the sealing members 112 and 119, The sealing performance at the time of the closing valve between the first and second valve bodies 110 and 117 is improved, and stable damping force characteristics are obtained. Particularly, in the hard characteristic region where the high pressure acts between the sealing members 112 and 119 and the valve seats 110 and 117 (the valve opening point A of the sub disc valves 111 and 118 shown in Fig. 8 112, and 119), the oil leakage can be prevented and the damping force characteristic can be stabilized. At this time, since the inner peripheral portion and the outer peripheral portion of the floating valve (one-kin, long f) are guided so as to extend along the retainers 133 and 134 so that the sealing portions 112a and 119a And the valve seats 110, 117, so that the seawater can obtain the sealing property

Next, a seventh embodiment of the present invention will be described with reference to Figs. 10 and 12. Fig.

The seventh embodiment is similar to the seventh embodiment in that the structure of the floating valve and its supporting means is almost the same except for the difference in structure. The same portions as those of the seventh embodiment are denoted by the same reference numerals and only different portions will be described in detail.

10, in the damping force generating mechanism 135 of the damper force adjusting type hydraulic buffer according to the seventh embodiment, the sealing portions 117a and 119a of the sealing members 112 and 117 are provided at the inner peripheral portion of the bladder portion provided with the sealing portions 117a and 119a Cylindrical guide dogs l 17b and l 19b are bent in the direction of the axial direction toward the valve member lof. Floating valves 135 and 137 as valve members are interposed between the sealing portions 117a and 119 of the sealing members 112 and 119 and the valve sheets 110 and 117 of the valve members 107 and 103, respectively. The floating valve 135. 137 is a flexible annular member as shown in Fig. 12, and is slidably fitted on the left outer circumference of the guide force l17b, l19b. And the other end thereof is in contact with the valve seats 110 and 117 of the valve members 102 and 103 and between the sealing member lIB and 117 and the valve seats 110 and 117 The flexibility of the floating valves 176 and 137 as in the sixth embodiment allows the sealing members 112 and 119 close to the rigid body to be in close contact with the valve seat 110 and 117. [ It is possible to improve the sealing performance at the time of the closing valve of the sealing members 112 and 117. Further, Since the floating valves 136 and 137 follow the sealing members 112 and 119 to be supported by the portions 12b and l19b, adhesion at the time of the closing valve is further improved and high sealing property can be obtained.

[Effects of the Invention]

As described in detail above. According to claim 1, by changing the passage area of the elongated variable orifice, the damping force characteristic before the opening of the elongated side main damping valve is directly adjusted and the spring pressure of the elongated side back pressure chamber is changed, It is possible to adjust the opening pressure of the valve and the driving force characteristic after the opening, and the valve characteristic can be obtained before the opening of the extension side main damping valve by the extension side damping valve. Further, by changing the passage area of the contraction-side variable orifice, the damping-force characteristic before the opening of the contraction-side main damping valve is directly adjusted and the internal pressure of the contraction- Damping force characteristics can be adjusted. The valve characteristic can be obtained before the shrinkage side main damping valve is opened by the shrinkage side damping valve. In addition, at the time of the contraction stroke, the flow of oil between the cylinder chamber and the reservoir is controlled to generate the damping force, so that the cylinder chamber does not become a negative pressure due to the flow resistance of the variable orifice and the damping valve, have. As a result, the adjustment range of the damping force characteristic can be widened, and in particular, the damping force characteristic in the low speed range of the piston speed can be optimized. Therefore, it is possible to effectively obtain the appropriate damping force characteristics in accordance with a low driving condition, and to effectively improve the hinge, the descent and the steering stability.

According to the damping force control type hydraulic buffer cushion of claim 2, since the plate spring constituting the weight damping valve and the disk valve constituting the sub-damping valve are laminated, the vibration thereof can be attenuated by the friction between the laminated members, It is possible to prevent the occurrence of jointing due to the above-mentioned problems. By setting the number of times of lapping of the disc valve appropriately, it is possible to obtain a desired flexible design and to exert an excellent effect that a subtle damping force adjustment can be performed in a low speed region of the piston speed.

According to the damping force-regulating hydraulic buffer according to the third aspect of the present invention, the plate spring and the disc valve can be jointly combined to reduce the manufacturing cost.

According to the damping force-regulating hydraulic buffer according to claim 4, by improving the valve member, the sealability between the valve body and the valve seat at the time of valve closing is improved, so that a stable damping force characteristic can be obtained.

One. The discs 111a and 111b constituting the sub disc valves 111 and 118 and the discs 11a and 11b 118a and 118b constituting the leaf springs 113 and 170 have the same diameter, By getting the original car by the flexibility. They can be used in common, and the manufacturing cost can be reduced.

Next, a sixth embodiment of the present invention will be described with reference to Figs. 9 and 11. Fig. The sixth embodiment is substantially the same as the fifth embodiment except for the structure of the extension side of the damping force adjusting mechanism and the structure of the main damping valve on the contraction side. In the second, seventh embodiments and red beans, the same numbers are attached to portions, and only the other portions are described in detail.

9, in the damping force generating mechanism 130 of the hydraulic shock absorber for adjusting the damping force according to the sixth embodiment, the sealing member 111, 119 and the burn sheets 110, 111 of the valve members 102, A floating valve 131, 132 as a valve member is stored. The floating valve (one long piece 13f) is a plastic annular member. The sliding groove is uniformly fitted on the outer periphery of a cylindrical retainer (one piece) 134 fixed to the guide member 107, and one end surface is sealed with sealing members 118 and 119 117 and the valve seat 110, 117 of the valve member 102, 103 and the valve seat 110, 117 of the valve member 102, 103, As shown in Fig.

As shown in FIG. A plurality of protruding portions 131a and 132a are formed in the inner circumferential portion of the blotting valve 137. The protruding portions 133a and 134a of the protruding portions 131a and 132a are inserted into the retaining portions 133 and 134, And is guided so as to be slidable in accordance with the moving direction of the sealing members 112 and 117. Floating valves (1, 132) Passages 135, 136 are formed between the retainers 133, 134. The fixed orifices (cutting forces 113c and 120c) of the leaf springs 113 and 170 are communicated with the extension side and the side of the contraction side passages 108 and 115 through the passages 135 and 137, respectively. The diameters of the sealing portions 117a and 117a of the sealing members 112 and 119 are smaller than the diameters of the valve sheets 110 and 117 of the valve member 107 and 103.

With this configuration, The seventh embodiment exhibits the same operation and effect.

Since the floating valves 131 and 137 having flexibility between the sealing members 117 and 119 nearly near the rigid body and the valve sheets 110 and 117 are opened, the sealing members 112 and 119 and the valve seat 110, and 117 can be improved, and a stable damping force characteristic can be obtained. Particularly, in the hard characteristic region where the high pressure acts between the sealing members 112 and 119 and the valve seats 110 and 117 (the valve opening point A of the sub disc valves 111 and 118 shown in Fig. 8 112, and 119), the oil leakage can be prevented and the damping force characteristic can be stabilized. At this time, the inner peripheral portion and the outer peripheral portion of the floating valve (one-kin, long f) are guided along the retainers 133 and 134 so as to be constantly spaced apart from each other, and the sealing portions 112a and 119a ) And the valve seats 110, 117, so that the seals can be made to have sealability

Next, a seventh embodiment of the present invention will be described with reference to Figs. 10 and 12. Fig.

The seventh embodiment is similar to the seventh embodiment in that the structure of the floating valve and its supporting means is almost the same except for the difference in structure. The same portions as those of the seventh embodiment are denoted by the same reference numerals and only different portions will be described in detail.

10, in the damping force generating mechanism 135 of the damping-force-regulating hydraulic buffer according to the seventh embodiment, the damping force generating mechanism 135 of the damping force adjusting type hydraulic buffer according to the seventh embodiment is provided with the sealing portions 117a and 119a of the sealing members 112 and 117, Cylindrical guide portions l17b and l19b are formed on the valve member lof 103 side in accordance with the axial direction. Floating valves 135 and 137 as valve members are provided between the sealing portions 117a and 119 of the sealing members 112 and 119 and the valve sheets 110 and 117 of the valve members 107 and 103, respectively. The floating valve 135. 137 is a flexible annular member as shown in Fig. 12, in which the sliding force is intermittently engaged with the guide forces l17b and l19b and the outer peripheral portion, And the other end thereof is in contact with the valve seats 110 and 117 of the valve members 102 and 103 and between the sealing member lIB and 117 and the valve seats 110 and 117 The flexibility of the floating valves 176 and 137 as in the sixth embodiment allows the sealing members 112 and 119 close to the rigid body to be in close contact with the valve seat 110 and 117. [ It is possible to improve the sealing performance at the time of the closing valve of the sealing members 112 and 117. Further, Since the floating valves 136 and 137 follow the sealing members 112 and 119 to be supported by the portions 12b and l19b, adhesion at the time of the closing valve is further improved and high sealing property can be obtained.

[Effects of the Invention]

As described in detail above. According to claim 1, by changing the passage area of the elongated variable orifice, the damping force characteristic before the opening of the elongated side main damping valve is directly adjusted and the spring pressure of the elongated side back pressure chamber is changed, It is possible to adjust the opening pressure of the valve and the driving force characteristic after the opening, and the valve characteristic can be obtained before the opening of the extension side main damping valve by the extension side damping valve. Further, by changing the passage area of the contraction-side variable orifice, the damping-force characteristic before the opening of the contraction-side main damping valve is directly adjusted and the internal pressure of the contraction- Damping force characteristics can be adjusted. The valve characteristic can be obtained before the shrinkage side main damping valve is opened by the shrinkage side damping valve. In addition, at the time of the contraction stroke, the flow of oil between the cylinder chamber and the reservoir is controlled to generate the damping force, so that the cylinder chamber does not become a negative pressure due to the flow resistance of the variable orifice and the damping valve, have. As a result, the adjustment range of the damping force characteristic can be widened, and in particular, the damping force characteristic in the low speed range of the piston speed can be optimized. Therefore, it is possible to effectively obtain the appropriate damping force characteristic according to the driving state of the vehicle, thereby effectively improving the hinge, ride comfort and steering stability.

According to the damping force adjustment type hydraulic buffer cushion of claim 2, since the plate spring constituting the main damping valve and the disk valve constituting the sub-damping valve are laminated, the vibration thereof can be attenuated by the friction between the laminated members, It is possible to prevent the occurrence of jointing due to the above-mentioned problems. In addition, by setting the number of laminated disc valves appropriately, desired flexibility can be obtained and subtle damping force adjustment can be performed in the low speed range of the piston speed.

According to the damping force-regulating hydraulic buffer according to the third aspect of the present invention, the plate spring and the disc valve can be jointly combined to reduce the manufacturing cost.

According to the damping force-regulating hydraulic buffer according to claim 4, by improving the valve member, the sealability between the valve body and the valve seat at the time of valve closing is improved, so that a stable damping force characteristic can be obtained.

According to the damping force-regulating hydraulic buffer of claim 4, since the valve member moves following the valve body, the adhesion between the valve body and the valve seat and the valve member can be further improved.

Claims (5)

A cylinder having an oil filled therein, a piston slidably mounted in the cylinder so as to divide the cylinder into two cylinder chambers, a piston rod having one end connected to the piston and the other end extended to the outside of the cylinder, A cylinder for storing a change in the volume of a cylinder connected to the piston rod and compensating for a change in the volume of the cylinder by compression and expansion of the gas; Side main passageway for circulating the oil from the cylinder chamber to the storage chamber at the time of the contraction stroke, an extension-side main damping valve for adjusting the passage area of the extension-side passage, and a valve body of the extension-side main damping valve Side back-pressure chamber for exerting an internal pressure in the direction of the closing valve and its elongation side back- Side extension valve for adjusting the passage area of the extension-side upstream passage by opening the valve at an expansion valve upstream passage communicating the cylinder chamber on the upstream side of the long-side main damping valve and an opening valve pressure lower than the expansion- And a downstream side passage for communicating the downstream side back-pressure chamber and the cylinder chamber on the downstream side of the downstream side main-damping valve, a variable-side orifice for regulating a passage area of the downstream-side passage and a passage area of the contraction- Side shunt back pressure chamber and the cylinder chamber on the upstream side of the shrinkage-side main damping valve communicate with the valve body of the shrinkage-side main damping valve, And the valve is opened at an opening valve pressure lower than the shrinkage-side main damping valve Side damping valve for adjusting a passage area of the shrinkage-side upstream passage, a downstream side passage for connecting the contraction-side back pressure chamber and the reservoir on the downstream side of the contraction-side damping valve, and a shrinkage- Side variable orifice, wherein the variable damper is provided with a variable-side orifice. 2. The valve seat according to claim 1, wherein the extension side and the shrinkage side main damping valve are provided with a valve body provided to be capable of advancing and retreating relative to the valve seat, and laminated leaf springs for pressing the valve body toward the valve seat side, Wherein the side damping valve is a laminated disc valve having an orifice passage. The damper hydraulic damper according to claim 2, wherein the plate spring is a disc-shaped plate, and the outer diameters of the leaf spring and the disc valve are the same. The damping force-regulating hydraulic shock absorber according to claim 2 or 3, wherein a flexible valve member is provided between the valve body and the valve seat so as to be movable forward and backward relative to the valve seat. The damping force-regulating hydraulic buffer according to claim 4, wherein the valve member is supported on the valve body. ※ Note: It is disclosed by the contents of the first application.