JPH0357340B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic shock absorber suitable for use in vehicles such as two-wheeled vehicles and four-wheeled vehicles.

This kind of conventional hydraulic shock absorber has a piston rod inserted into the cylinder via a piston, a reservoir is provided on the outside of the cylinder, and the piston forms two upper and lower oil chambers in the cylinder, with the lower oil chamber having a base valve. It is known that the piston part has a through hole through which two oil chambers (upper and lower) communicate with the reservoir, and a valve provided at the mouth end of the through hole.

However, in the base valve of the above-mentioned hydraulic shock absorber, the valve for generating the compression side damping force and the suction check valve are separately built into the housing, and the overall wall thickness and length in the axial direction are long and the structure is complicated. Therefore, by incorporating this base valve, the basic length of the hydraulic shock absorber itself becomes longer.

Furthermore, a conventional hydraulic shock absorber is known in which the damping force is variably adjusted by selectively passing one of a plurality of orifices having different diameters in the middle of the passage.

A hydraulic shock absorber is also known in which a suspension spring is interposed between the piston rod and the cylinder, and the initial set load of the suspension spring is arbitrarily adjusted from the outside.

However, it is extremely difficult to simultaneously perform the above damping force adjustment and spring load adjustment with a single touch.

SUMMARY OF THE INVENTION Accordingly, a first object of the present invention is to provide a hydraulic shock absorber which has a simple structure and whose basic length can be shortened.

A second object of the present invention is to provide a hydraulic shock absorber that can be added to a hydraulic shock absorber for miscellaneous trees and independently adjust the damping force or spring load.

A third object of the present invention is to provide a hydraulic shock absorber in addition to the above-mentioned hydraulic shock absorber, which allows damping force adjustment and spring load adjustment to be performed manually and simultaneously with a single touch.

Similarly, a fourth object of the present invention is to provide a hydraulic shock absorber in which damping force adjustment and spring load adjustment can be easily and remotely performed in addition to the above-mentioned hydraulic shock absorber.

In order to achieve the above first object, the configuration of the first specific invention is such that the cylinder, the outer tube, the passage outside the cylinder, and the reservoir are integrally molded in a honeycomb type, and the bearing that guides the piston rod is used to generate rebound damping force. A leaf valve is provided at the bottom of the cylinder, and a valve body for the compression side damping force generation valve and a valve body for checking the suction port from the oil chamber to the cylinder that communicates with the reservoir are formed on one leaf valve at the bottom of the cylinder. It is characterized by the fact that

In order to achieve the second objective, in addition to the configuration of the specific invention, an adjustment cam for adjusting the damping force is provided on the outside of the outer tube so as to be movable in the rotational direction, and the opening area of the oil passage is set on this adjustment cam by hardening. It is characterized by having a means for changing it into three levels: , medium, and soft.

In addition to the configuration of the specific invention, the configuration for achieving the third objective is to provide a damping force adjustment cam on the outside of the outer tube so as to be movable in the vertical and rotational directions, and to interlock with the damping force adjustment cam on the outside of the damping force adjustment cam. An adjustment dial is provided to be movable up and down and in the rotational direction, and a suspension spring is supported on the upper part of the adjustment dial,
Further, a cam member having a plurality of cam surfaces provided at the bottom thereof is provided so as to be movable in the rotation direction and the vertical direction, and a stopper is selectively fitted to one of the cam surfaces. .

Furthermore, in order to achieve the fourth object, in addition to the configuration of the specific invention, a damping force and spring load adjustment member is provided on the outside of the outer tube so as to be movable up and down, and a hydraulic power source is provided below the spring load adjustment member. The invention is characterized in that an oil chamber is formed which is connected to the oil chamber, and hydraulic pressure is remotely supplied to and discharged from the oil chamber.

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a sectional view of a hydraulic shock absorber according to an embodiment of the specific invention, which is characterized in that a bearing portion 1 and a bottom portion 3 are provided with leaf valves 2 and 4 for generating damping force. It is.

To explain this in more detail, a piston rod 7 is slidably inserted into the cylinder 5 via a piston 6, the piston rod 7 penetrates the bearing part 1 and the seal 8, protrudes to the outside, and has a cushion 9 and a bracket 10 at the tip. is installed.

An outer tube 11 concentric with the cylinder 5 is provided outside the cylinder 5, and a bearing portion 1 and a seal 8 are provided at the upper ends of the cylinder 5 and the outer tube 11.
is held, and the bottom part 3 and bracket 1 are held at the lower end.
2 is retained.

As shown in FIG. 2, the cylinder 5 and the outer tube 11 are integrally formed by extrusion molding or the like in a so-called honeycomb type. Inside the cylinder 5 are two oil chambers 1, upper and lower, separated by a piston 6.
3 and 14 are partitioned, and between the cylinder 5 and the outer tube 11 there are two opposing oil chambers 15,
16 and reservoirs 17, 18 are formed, and these oil chambers 15, 16 and reservoirs 17, 18 are integrally molded when the cylinder 5 and outer tube 11 are molded.

The bearing part 1 consists of a valve seat 19 and a valve holder 20, and a disc-shaped leaf valve 2 is held between the valve seat 19 and the valve holder 20.

Two through holes 21 and 22 are formed in the valve seat 19 in the axial direction as shown in FIG. The lower end opens into the oil chamber 15, and the upper end of each through hole 21, 22 opens into the lower end groove 23 of the valve holder 20 via the leaf valve 2, as shown in FIG.

As shown in FIG. 3, a tongue-shaped valve body 25 is formed in the leaf valve 2 by hollowing out a U-shaped opening 24, and a through hole 2 is formed at the base end of the valve body 25.
6 is bored, the valve body 25 contacts the opening end of the through hole 21 of the valve seat 19 in a freely openable/closable manner, and the through hole 26 similarly faces the through hole 22 of the valve seat 19.

The bottom part 3 has a valve seat 27 and a valve holder 2
8, a valve seat 27 and a valve retainer 2
A leaf valve 4 is sandwiched between the valves 8 and 8.

As shown in FIG. 7, the valve seat 27 has one discharge port 29 and two suction ports 2 in the axial direction.
9a, 29b and three tank ports 30, 30
a, 30b, and an annular groove 31 is provided on the upper surface of the valve seat 27, and the annular groove 31 is connected to the oil chamber 15.
is communicated with reservoirs 17 and 18.

Similarly, the annular groove 31 connects the oil chamber 16 to the reservoir 17,
18 and also communicates with the tank port 30.

As shown in FIG. 6, the leaf valve 4 consists of a single disk, and there are three U-shaped openings 3 in the disk.
3, 34, and 35 are hollowed out to form three tongue-shaped valve bodies 36, 37, and 38 in the center, respectively. Valve bodies 36 and 37 are reservoir 1
It is used as a valve element for checking the suction port by contacting the lower end of the tank ports 29a and 29b leading to the ports 7 and 18 so as to be openable and closable. It is used as a valve body for generating compression side damping force by coming into contact with it. The leaf valve 4 has two ports 39 and 40 near the center, and a port 41 at the base end of the valve body 38. Through the oil chamber 14, another port 41 communicates with the reservoirs 17, 18 via a tank port 30 and an annular groove 31.

Grooves 42a, 42b, 42c are formed on the upper surface of the valve holder 28, facing the valve bodies 36, 37, 38 and the openings 33, 34, 35 of the leaf valve 4.
Within these grooves 42a, 42b, 42c, the valve bodies 36, 3
7 and 38 are designed to be flexible.

In the bearing part 1, positioning means a and b such as holes or curved parts are formed between the valve seat 19, the leaf valve 2, and the valve holder 20, as shown in FIG. It is designed to allow a pin or ball to be inserted.

Similarly, in the bottom part 3, between the valve seat 27, the leaf valve 4, and the valve holder 28, there is a positioning means c consisting of a hole or a curved part, etc., as shown in FIG.
are formed, and these holes or curved portions are connected to each other while being positioned through pins, balls, etc.

A through hole 44 is vertically bored in the piston 6 to allow the upper and lower oil chambers 13 and 14 to communicate with each other, and a leaf valve is installed at the upper end of the through hole 44 to generate a damping force on the rebound side and also serves as a compression side suction check valve. 45 is arranged to be openable and closable, and a cushion spring 47 is provided above the valve holder 46 above the piston 6.

Next, we will discuss the operation.

During the extension operation in which the piston 6 rises, a portion of the oil in the upper oil chamber 13 flows into the leaf valve 45 of the piston section.
The oil flows out from the through hole 44 into the lower oil chamber 14 through the hole provided in the valve seat 19, and some oil flows into the through hole 21 of the valve seat 19.
As a result, the valve body 25 of the leaf valve 2 is bent upward, and the oil flows out from the opening 24 into the groove 23 of the valve holder 20, and the oil in this groove 23 flows through the through hole 26 of the leaf valve 2 and the hole 22 of the valve seat. The oil in the oil chamber 15 flows out into the oil chamber 15, and the oil in the oil chamber 15 flows into the reservoir 1 through the annular groove 31 of the valve seat 27 in the bottom part 3.
Returned to 7,18. At this time, a damping force on the extension side is generated by the flow resistance of the hole in the leaf valve 45 in the piston portion and the deflection action of the valve body 25.

Furthermore, the oil in the reservoirs 17 and 18 is transferred to the tank ports 30a and 3 of the valve seat 27 in the bottom part 3.
0b, bend the valve bodies 36, 37 of the leaf valve 4, pass through the grooves 42a, 42b of the valve holder 28, and then pass through the ports 39, 40 of the leaf valve 4 and the suction ports 29a, 29b of the valve seat 27 to the lower part. The oil is sucked into the oil chamber 14, thereby compensating the amount of oil corresponding to the protruding volume of the piston rod 7.

Next, in the pressure side operation in which the piston 6 descends, part of the oil in the lower oil chamber 14 is supplied to the upper oil chamber 13 through the through hole 44 of the piston 6 by deflecting the leaf valve 45, and the amount of intrusion of the piston rod 7 The volume of oil is discharged from the port 29 of the valve seat 27 into the groove 42c of the valve holder 28 by bending the valve body 38 of the leaf valve 4, and the oil in the groove 42c is further discharged from the port 41, the port 30, and the annular groove 31. The water is returned to the reservoirs 17 and 18 via. At this time, a compression damping force is generated due to the deflection of the valve body 38.

In the above hydraulic shock absorber, the cylinder body is integrally molded in a honeycomb style, so it is easy to mold.
The structure is simple. Since only one leaf valve is installed in the bearing and bottom parts, the structure is simple, and the base valve in particular has a separate valve for generating compression damping force and a suction check valve, unlike conventional models. Since the leaf valve is used as a single leaf valve instead of a single leaf valve, the overall length is thinner and the basic length of the cylinder can be shortened.

Next, FIG. 9 is a sectional view of a hydraulic shock absorber according to an embodiment of the second invention.

This is a hydraulic shock absorber according to the first invention with a damping force adjustment mechanism attached, and the main body of the hydraulic shock absorber is substantially the same as that in Fig. 1, so the same reference numerals are given. A detailed explanation of the structure will be omitted.

However, the difference from the one in Fig. 1 is that the bottom side valve seat 27 is not provided with the same annular groove 31 as in Fig. 1,
The oil chambers 15 and 16 communicate with reservoirs 17 and 18 via damping force adjustment mechanisms, respectively.

Further, projections 48 and 49 are provided on the end surfaces of the upper and lower valve seats 19 and 27, respectively, and these projections 4
The valve seats 19 and 27 can be positioned by inserting the valve seats 8 and 49 into the mouth ends of the oil chambers 16 and 15, respectively. All other configurations are the same as in FIG. 1.

The gist of the second invention is that the damping force adjustment device 50 is provided outside the outer tube 11.

That is, an adjustment cam portion 51 for adjusting the damping force is provided at the outer lower part of the outer tube 11 so as to be movable in the rotational direction and the vertical direction. The adjustment cam part 51 includes a cylindrical body 52, a flange part 53 integrally connected to the upper part of the cylindrical body 52, and step parts A, B, C, D, and E in five stages formed at the lower part of the cylindrical body 52. ,
It consists of three sets of orifices P1, P2, P3, . . . Pn with different diameters provided at the stepped portions A, B, C, D, and E (Figs. 11 and 16).

A sleeve 54 is provided on the outside of the cylindrical body 52 so as to be movable in the rotational direction and the vertical direction.
There is a spacer 55 and a cylindrical adjustment dial 5 on the outside of the
6 are fitted to be rotatable and movable up and down, and by caulking the upper end of the adjustment dial 56, the flange 53 of the cam portion 51 is held together with the sleeve 54.

Adjustment dial 56, spacer 55 and sleeve 5
A cylinder 57 serving as a rotational driving member is fitted into the cylinder 57 from the outside in the radial direction.
When a tool is inserted into the holder and a force in the rotational direction is applied, the adjustment dial 56, spacer 55, sleeve 54, and adjustment cam 51 rotate together in the same direction and by the same amount.

The orifices P1, P2, P3, .

The outer tube 11 is formed with a port 59 for generating a rebound damping force that faces the adjustment cam 51, a port 60 for generating a compression damping force, and tank ports 61, 62, and the port 59 opens into the oil chamber 15. Any one orifice P of the cylindrical body 52
1, P2, . It opens into a gap 63 through any one of P1, P2...Pn, and this gap 63 opens into the reservoir 18 through a port 62.

As shown in FIGS. 11 and 16, the adjustment cam 51 includes a plurality of stepped portions A, B, C, D, and E, and orifice groups P of three diameters are provided in each of the stepped portions. It is possible to use the embodiments shown in FIGS.

Figure 12 shows a group of steps Q with different heights in each step.
Q1, Q2, Q3...Qn are formed as shown in FIG. Slit group S with different widths and depths
S1, S2...Sn are formed as
Further, in FIG. 15, notches T1, T2, .
One of these step group Q, taper group R, slit group S, and notch group T is port 59,
The purpose is to change the opening area of the ports 59 and 60 when facing the port 60, and to generate a damping force corresponding to the size of the opening area.

Furthermore, a cam member 64 is inserted into the outer periphery of the lower end of the outer tube 11 so as to be movable in the rotational direction and the vertical direction.A cam stopper 65 is disposed at the lower part of the cam member 64. It is inserted into the bracket 12 and fixed to the base end of the bracket 12 by welding or the like.

The cam member 64 has a cylindrical body 6 as shown in FIG.
7, an upper end flange 68 of the cylindrical body 67, and a cam group W consisting of a plurality of cam surfaces W1, W2...Wn of different heights formed at the lower part of the cylindrical body 67,
Recesses 69 are formed at a plurality of positions on the upper surface of the flange 68, and a cutout groove 70 of a desired width is formed on the outside of the flange 68.

A protrusion 71 is formed downward at the lower end of the adjustment dial 56, and this protrusion 71 is connected to the cam member 6.
It is inserted into the notch groove 70 of No. 4 so as to be movable in the rotational direction.

The cam stopper 65 has two claws 73 standing up on the upper part of the plate body 72, and legs 74 are vertically provided on the lower part.
are selectively fitted to any one of the cam surfaces W1, W2...Wn of the cam member 64, and the legs 74 are fitted to one of the cam surfaces W1, W2...Wn of the cam member 64.
It is inserted into the outer periphery of 6 and fixed by welding or the like.

A detent ball 75 is interposed between the spacer 55 and the cam member 64, and this ball 75 is selectively fitted into one of the recesses 69 of the cam member 64 to position the spacer 55 and the adjustment cam 51 connected thereto. The decision is now being made.

When the adjustment dial 56 is rotated via the cylindrical body 57 fitted to the adjustment dial 56, if the protrusion 71 moves within the notch groove 70 in the cam member 64 within the range of angle θ, the adjustment cam 51 In this case, the opening area adjustment means such as an orifice in any one step is hard or
It switches only to three stages: medium and soft.

If you wish to use another step opening area adjustment means, manually rotate the cam member 64 or rotate the cylindrical body 57 by an angle of θ or more, so that the cylindrical body 57 aligns with the end surface of the notch groove 70. The cam member 64 may be rotated at this time. In this case, the pawl 73 of the stopper 65 that has been fitted to an arbitrary cam surface of the cam group W is fitted to one of the other cam surfaces, and thereby the height of the selected cam surface is adjusted. The cam member 64 is displaced in height, and at this time, the height of the adjusting cam 51 is also displaced via the spacer 55 and the sleeve 54, and the adjusting means of the stepped portion corresponding to this height is opposed to the through hole 59. A damping force corresponding to this adjustment means can be obtained.

By the way, the adjustment cam 51 has a plurality of stepped portions A, B,
When C, D, and E are provided, a height adjusting member such as the cam member 64 is required to select one of the stepped portions, but by rotating the adjusting cam 51, If a plurality of opening area adjusting means such as orifices are provided and only one of these means needs to be selected, only the adjusting cam 51 needs to be rotated. In this case, the cam member 64 is not necessary and it can be It can also be used simply by fixing it below the tube 11 as a support member.

Next, the operation when adjusting the damping force via the damping force adjusting device 50 described above will be described.

Now, as shown in FIG. 16, the stepped portion C of the adjustment cam 51 is in a position facing the ports 59 and 60 of the outer tube 11, and the orifice P8 is open to the ports 59 and 60, respectively, and the cam member It is assumed that the cam surface W2 of 64 is fitted into the claw 73.

When the piston 6 extends in this state, the oil in the oil chamber 13 above the piston flexes the valve body 25 of the leaf valve 2 through the through hole 21 and flows out through the opening 24 into the groove 23. The oil flows through the through hole 22 - the oil chamber 15, the port 59, and the orifice P of the adjustment cam 51.
8, reservoir 17 via gap 63 and port 61
will be returned to.

Further, a part of the oil in the oil chamber 13 flows out into the lower oil chamber 14 through the orifice in the leaf valve 45 of the piston 6.

In the above flow, the valve body 2 of the leaf valve 2
A synthetic rebound damping force is generated by the resistance due to the deflection of the leaf valve 45, the flow resistance of the orifice P8, and the flow resistance of the orifice of the leaf valve 45. Furthermore, the oil in the reservoir 18 is transferred to the bottom part 3 through ports 30a,
30b, the valve bodies 36, 37 of the leaf valve 4 are bent and sucked into the grooves 42a, 42b, and further passed through the suction ports 29a, 29b to the lower oil chamber 14.
This compensates for the amount of oil corresponding to the protruding volume of the piston rod 7.

Next, in the compression operation in which the piston 6 descends, the oil in the lower oil chamber 14 flows out from the through hole 44 of the piston 6 into the upper oil chamber 13 by bending the leaf valve 45 upward, and the amount of entry of the piston rod 7 The amount of oil flows from the lower oil chamber 14 to the port 29, further bends the valve body 38 of the leaf valve 2, and flows out into the groove 42c. Boat 60, orifice P8,
It flows out into the reservoir 18 through the gap 63 and the port 62, and in the above flow, a damping force on the pressure side is obtained by the bending resistance of the valve body 38 and the flow resistance of the orifice P8.

Incidentally, the adjustment cams 51 are two identical ones shown in the exploded views of FIGS. 11 to 15, which are successively formed symmetrically, and each adjustment means is connected to a port 59 and a port 6.
0, but the adjustment means can be combined arbitrarily; for example, on the expansion side, the orifice P
1, P2...Pn, and the compression side can be adjusted using the step group Q and the tapered surface group R.

Port 5 of outer tube 11 as above
When ports 9 and 60 face orifice P8 of adjustment cam 51, damping force characteristics corresponding to the opening area of orifice P8 are obtained;
0 to orifice P with a larger diameter than orifice P8
If it is placed opposite to orifice P9, soft characteristics will be obtained corresponding to orifice P9, whereas if it is placed to face orifice P7, hard characteristics will be obtained.

In this case, insert a tool into the hole 58 of the cylindrical body 57 and insert the cylindrical body 57 into the notch groove 7 of the cam member 64.
It is sufficient to rotate in either direction within the range of 0, in other words, within the range of angle θ. That is, for example, when the cylinder 57 is rotated clockwise within the range of angle θ, the adjustment dial 56, spacer 55, sleeve 54, and adjustment cam 51 are rotated in the same direction and by the same amount, and at this time, the orifice P9 of the adjustment cam 51 is rotated to the port 59, 60. You will be facing this.

Furthermore, since the orifices P7, P8, and P9 are provided in the step C, for example, if one of the orifices in the upper step D is opposed to the ports 59 and 60, the cylinder 57 is rotated at an angle of θ or more. When the switching cam 64 is rotated clockwise or counterclockwise by an angle θ or more, the adjustment dial 56, spacer 55, sleeve 54, and adjustment cam 51 are also rotated in the same direction and by the same amount in conjunction with the switching cam 64. Rotate. At this time, the cam surface of the cam member 64 is displaced from the cam surface W3 to the cam surface W2, and this cam surface W2 fits into the pawl 73 of the stopper 65. In this case, the claw 73 transfers from the cam surface W3 to the cam surface W2 because the cam member 64 is lowered by the difference in height between the cam surfaces W3 and W2, and the adjustment cam 51 is also lowered by the same amount, and the upper step Part D orifice is port 59,6
It will face 0.

The adjustment cam 51 and the like are lowered by the main spring force of a damper (not shown) (shown in FIG. 18).

Also, the orifices P4, P5, P6 of the lower step B
If you want to face either of them, just rotate it in the opposite direction.

When the adjustment dial 56 and the spacer 55 rotate in the rotational direction, the positioning recess 6 corresponding to the position
The detent port 75 is fitted and positioned in the cam 9, thereby preventing the adjustment cam 51 from shifting.

Next, FIG. 18 is a sectional view of a hydraulic shock absorber according to a third embodiment of the invention.

This is substantially the same as the hydraulic shock absorber shown in FIG. 9, in which a suspension spring is interposed between the piston rod and the adjustment dial, and a rotary drive member is attached to the cam member, and in addition, the hydraulic shock absorber shown in FIG. In the embodiment, the cam member can be of a fixed type, whereas in the embodiment shown in FIG. 18, it is essential that the cam member is movable in the vertical direction and in the rotational direction. The other configurations and operations are exactly the same as in the case of FIG. 9, so details will be omitted.

In FIG. 18, a spring seat 76 is provided at the outer end of the piston rod 7, and a cover 77 is provided downward from the end of the spring seat.

Further, a spring seat 79 is provided above the adjustment dial 56, and two spring seats 76, 79 are provided.
A suspension spring 78 is interposed between them, and this suspension spring 78 always urges the piston rod 7 in the direction of extension.

Further, a cylindrical body 80 serving as a driving member is provided on the outer periphery of the cam member 64 and projects laterally, and a tool can be inserted into a hole 81 of the cylindrical body 80 to rotate the cam member 64 in one direction.

Describing the operation of the above embodiment, the first point is that it rotates with the cylindrical body 57, selects one of the opening area adjusting means of the adjusting cam 51, and obtains an expansion/compression damping force according to the selected means. This is exactly the same as in Figure 9.

Next, when a tool is inserted into the cylindrical body 80 of the cam member 64 and the cam member 64 is rotated in one direction, one of the cam surfaces of the cam member 64 engages with the pawl 73, and the height of the selected cam surface is adjusted. The cam member 64, adjustment dial 56, and adjustment cam 51 are moved to corresponding heights. Therefore, one of the steps corresponding to the height of the adjustment cam 51 is selected, and the damping force of expansion and compression is set according to the opening area adjustment means provided in this step, and the adjustment dial 56 is raised or The initial setting load of the suspension spring 78 changes by the amount of descent.

Therefore, in the embodiment shown in FIG. 18, when the cam member 64 is manually rotated through the cylindrical body 80, the damping force adjustment and the spring load are adjusted at the same time, and there is no need to take the trouble to provide two adjustment members, resulting in a simple structure. This is the result.

Next, FIG. 19 relates to an embodiment of the fourth invention, which is added to the configuration of the specific invention so that damping force adjustment and spring load adjustment can be performed continuously.

In this case, an outer cylinder 82 is fixed to the outer lower part of the outer tube 11, a free piston 83 is slidably inserted between the outer cylinder 82 and the outer tube 11, and an oil chamber 84 is provided in the lower part of the free piston 83. This oil chamber 84 is divided into sections, and this oil chamber 84 is connected to a port 85 provided in the outer cylinder 82.
A suspension spring 78 is interposed between a spring seat 86 provided on the upper part of the free piston 83 and a spring seat 76 on the piston rod 7 side.

Grooves 87 and 88 are formed on the inner surface of the free piston 83.
The grooves 87 and 88 communicate with the reservoirs 17 and 18, respectively. The outer tube 11 has a plurality of orifices 01, 02, 03, 04 facing the grooves 87, 88, and an orifice 0.
5, 06, 07, and 08.

A pipe 89 made of urethane or other synthetic resin is fitted into the upper part of the oil chamber 15, and a filler 90 made of the same material is fitted into the upper part of the other oil chamber 16.

In the above-mentioned hydraulic shock absorber, during the extension operation, the oil in the oil chamber 15 flows out into the groove 87 through one or more of the orifices 01, 02... It is returned to the reservoir 17 via the hole.

Also, during compression operation, the oil in the lower oil chamber 14 enters the oil chamber 16 through the leaf valve 2, and the oil in this oil chamber 16 is introduced into the groove 88 through one or more of the orifices 04, 05...08, The oil in this groove 83 is returned to the reservoir 18 through a hole bored in the outer tube 11.

The damping force on the expansion side or the compression side is obtained by the flow resistance due to the total area of the orifices 01, 02...04 or the orifices 05, 06...08.

On the other hand, when high pressure is supplied from the pump to the port 85 to the oil chamber 84 by remote control, the free piston 83 rises against the suspension spring according to the amount of oil, and the oil supply is stopped at an arbitrary position, and the oil chamber 84 When the pressure is maintained, the free piston 83 stops at that position. As a result, the suspension spring 78 is compressed, and this state is set as the initial load.

Also, at this time, the inner periphery of the free piston 83 is simultaneously connected to the orifices 01, 02...04, the orifices 05,
Since any one of 06...08 is blocked, the opening area of the orifice becomes smaller.

Conversely, connect port 85 to the tank side and open oil chamber 84.
If some or all of the oil is discharged, the free piston 83 will descend accordingly, making the spring load weaker and the damping force softer, which can be adjusted.

In the above case, the spring load adjustment and the damping force adjustment can be performed simultaneously with one device, and these operations can be performed remotely, making the operation easy.

As described above, in the first specific invention, one leaf valve is interposed in the bottom part, and this leaf valve is provided with a valve body for generating a compression side damping force and a valve body for suction check on the rebound side. The valve has a simple structure, can be formed thin, and is easy to install. For this reason, the entire bottom part of the hydraulic shock absorber becomes thinner, and this basic length can be shortened.

Furthermore, since the cylinder, outer tube, oil chamber, and reservoir are integrally molded in a honeycomb type, the hydraulic shock absorber is easy to assemble and has a simple structure, light in weight, and low in cost. It is something.

In the second invention, since a damping force adjustment device is provided in addition to the configuration of the specific invention, the damping force on the expansion side and the compression side can be adjusted independently.

In addition to the configuration of the specific invention, the third invention provides a damping force adjustment device and a spring load adjustment device consisting of one mechanism, and by rotating one cam member, the damping force adjustment and the spring load adjustment can be performed simultaneously. Since it can be done with one touch, only one operation process is required, which significantly improves work efficiency.Also, since there is no need to provide separate adjustment devices for each, the structure is simplified, manufacturing and assembly are easy, and costs can be reduced. It is.

Furthermore, in the fourth invention, in addition to the specific invention, the damping force adjustment mechanism and the spring adjustment mechanism are combined in one device and can be operated at the same time, and the adjustment operation can be performed remotely using hydraulic pressure, so that the operation is easy. Become.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional front view of a hydraulic shock absorber according to an embodiment of the specific invention, FIG. 2 is a cross-sectional plan view taken along the - line in FIG. 1, FIG. 3 is a plan view of the leaf valve in the bearing section, and FIG. 4 is a bottom view of the valve holder in the bearing part, Fig. 5 is a plan view of the bearing, Fig. 6 is a plan view of the leaf valve in the bottom part, Fig. 7 is a bottom view of the valve seat in the bottom part, and Fig. 8 is a bottom view of the valve seat in the bottom part. FIG. 9 is a longitudinal sectional front view of a hydraulic shock absorber according to an embodiment of the second invention; FIG. 10 is a cross-sectional plan view taken along the - line in FIG. 9; Figure, 13th
14 and 15 are respectively exploded views of one embodiment of the adjustment cam, FIG. 16 is a perspective view of the cam member, FIG. 17 is an exploded perspective view of the adjustment dial, cam member, and stopper, and FIG. The figure is a longitudinal sectional front view of a hydraulic shock absorber according to an embodiment of the third invention, and FIG. 19 is a longitudinal sectional front view of a hydraulic shock absorber according to an embodiment of the fourth invention. 3...Bottom part, 4...Leaf valve, 5...
Cylinder, 6... Piston, 7... Piston rod, 11... Outer tube, 13, 14, 1
5, 16... Oil chamber, 17, 18... Reservoir, 2
7... Valve seat, 28... Valve holder, 2
9, 29a, 29b, 30, 30a, 30b...
Through hole, 36, 37... Valve body for checking the suction port, 38... Valve body for generating compression side damping force, 42a,
42b, 42c...Groove, 51...Adjustment cam, 56
...Adjustment dial, 59,60...Through hole, 64...
...Cam member, 65...Stopper, 73...Claw, 7
8...Suspension spring, 83...Free piston, 84...Oil chamber, O1, O2...On...Orifice, W1, W2,...Wn...Cam surface.

Claims (1)

[Claims] 1. An outer tube is provided concentrically with the cylinder,
A plurality of oil chambers and a plurality of reservoirs were formed between the cylinder and the outer tube, and the oil chambers and the reservoirs were made to communicate with each other, and a piston rod was slidably inserted into the cylinder via a piston. In a hydraulic shock absorber, a single leaf valve is installed at the bottom of the cylinder and outer tube, and this leaf valve has a valve body for generating compression side damping force, and a suction port from the oil chamber communicating with the reservoir to the cylinder. Hydraulic shock absorber equipped with a valve body for checking. 2. The hydraulic shock absorber according to claim 1, wherein the cylinder, outer tube, oil chamber, and reservoir are integrally molded in a honeycomb manner. 3. The bottom part consists of a valve seat, a valve holder, and a leaf valve interposed between the valve seat and the valve holder, and the valve seat has a through hole that allows the oil chamber at the bottom of the piston to communicate with the reservoir.
2. The hydraulic shock absorber according to claim 1, wherein the through hole is opened and closed by a valve body of a leaf valve, and the valve holder is further provided with a groove in which the valve body can bend. 4 Provide an outer tube concentrically with the cylinder,
A plurality of oil chambers and a plurality of reservoirs were formed between the cylinder and the outer tube, and the oil chambers and the reservoirs were made to communicate with each other, and a piston rod was slidably inserted into the cylinder via a piston. In a hydraulic shock absorber, a single leaf valve is installed at the bottom of the cylinder and outer tube, and this leaf valve has a valve body for generating compression side damping force, and a suction port from the oil chamber communicating with the reservoir to the cylinder. a valve body for checking, a through hole communicating with the oil chamber is bored in the outer tube, an adjusting cam is rotatably provided on the outside of the outer tube, and means for adjusting the opening area of the through hole on the adjusting cam. A hydraulic shock absorber having a through hole communicating with the reservoir through this means. 5 The opening area adjusting means is an orifice, a step,
The hydraulic shock absorber according to claim 4, which is a slit or a notch. 6 Provide an outer tube concentrically with the cylinder,
A plurality of oil chambers and a plurality of reservoirs were formed between the cylinder and the outer tube, and the oil chambers and the reservoirs were made to communicate with each other, and a piston rod was slidably inserted into the cylinder via a piston. In a hydraulic shock absorber, a single leaf valve is installed at the bottom of the cylinder and outer tube, and this leaf valve has a valve body for generating compression side damping force, and a suction port from the oil chamber communicating with the reservoir to the cylinder. A through hole communicating from the oil chamber to the reservoir is provided in the outer tube, and an adjusting cam is provided on the outside of the outer tube so as to be movable vertically and in the rotational direction. A means for adjusting the opening area is provided, an adjustment dial is provided that is movable up and down and in the rotational direction, and is interlocked with the adjustment cam, a suspension spring is provided at the top of the adjustment dial, and a suspension spring is provided at the bottom of the adjustment dial, and the adjustment dial is interlocked with the adjustment dial. A hydraulic shock absorber including a cam member, a plurality of cam surfaces provided at the lower part of the cam member, and a claw of a stopper fixed below selectively fitted into one of the cam surfaces. 7. The hydraulic shock absorber according to claim 6, wherein the adjusting cam is provided with a plurality of steps corresponding to the cam surface, and each step is formed with an orifice, step, slit, or notch. 8 A protrusion is provided at the bottom of the adjustment dial, a notch groove is provided on the cam member into which the protrusion is inserted, and the adjustment cam is rotated via the adjustment dial within the range of this notch groove, and beyond the range of this notch groove. Claim 6: When the cam member is rotated, the cam member also rotates in conjunction with the cam member.
Hydraulic shock absorber as described in section. 9 Provide an outer tube concentrically with the cylinder,
A plurality of oil chambers and a plurality of reservoirs are formed between the cylinder and the outer tube, and the oil chambers and the reservoirs communicate with each other, and a piston rod is slidably inserted into the cylinder via a piston. In the shock absorber, a single leaf valve is installed at the bottom of the cylinder and outer tube, and this leaf valve includes a valve body for generating compression side damping force and a suction port from the oil chamber communicating with the reservoir to the cylinder. a check valve body, and the outer tube is provided with one or more orifices communicating with the oil chamber,
A free piston is disposed on the outside of the outer tube so as to be able to move up and down, a groove is provided inside the free piston to allow the orifice to communicate with the reservoir side, and a suspension spring is provided on the upper part of the free piston. A hydraulic shock absorber with an oil chamber connected to the hydraulic power source at the bottom.