JPS63231030A - Damping-factor variable type shock absorber - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application] The present invention relates to a hydraulic damper (shock absorber), and particularly to an electrically controlled variable damping rate shock absorber.

[Prior art]

A vehicle's hydraulic damper is usually called a shock absorber, and it is desired to change its damping rate (stiffness) to adapt it to various road conditions and various driving modes.

Various types of electrically controlled shock absorbers are already known. U.S. Patent No. 2,507,2
The hydraulic damper described in No. 76 uses a solenoid-driven valve to increase its verticality in response to the braking force of the vehicle, and is designed to prevent the front of the vehicle from sinking during sudden stops. ing. In the hydraulic shock absorber described in U.S. Pat. No. 3,039,566, a solenoid-operated valve simultaneously communicates the upper and lower working chambers with a reservoir, and in the hydraulic shock absorber described in U.S. Pat. The damper (shock absorber) opens and closes a piston bypass passage connecting the upper and lower working chambers by operating a solenoid-driven rotary valve.

[Summary of the Invention] In the variable damping rate shock absorber of the present invention, a closing amount actuating cylinder is surrounded by an external housing to form a fluid reservoir, and a piston member divides the inside of the actuating cylinder into an upper working chamber and a lower working chamber. A hollow strut is slidably fitted into the working cylinder, one end of the strut is connected to the piston, and the other end is extended to the outside of the working cylinder. A telescoping cylinder is disposed within the hollow strut, one end of which communicates with the reservoir, the other end of which is slidably fitted into the hollow strut via a piston, and a solenoid valve means is disposed within the hollow strut. and connected to the other end of the telescoping cylinder, and the solenoid valve means is provided with an inlet port that communicates with the upper working chamber and an outlet port that communicates with the reservoir through the interior of the telescoping cylinder. It is characterized by

The variable damping rate shock absorber of the present invention has the advantage that the stiffness in both contraction and extension operations can be changed using a single solenoid valve. Another advantage is that the fluid flows in a single direction through the solenoid valve, allowing the use of fast-acting poppet-type valves, allowing the stiffness of the shock absorber to be varied during the compression and extension strokes.

〔Example〕

Next, the present invention will be explained in detail with reference to the drawings.

1 and 2 show details of a single solenoid type variable damping rate shock absorber.

In FIG. 1, the shock absorber 10 has a cylindrical outer housing 12 (outer shell) having a closing portion 14.
is the provision. An inner cylinder 16 is provided inside the housing 12 . One end of the cylinder 16 is the closed end 1
4 is closed by a two-way pressure relief valve member 18. The relief valve member 18 connects the interior 20 of the inner cylinder 16 and the cylindrical reservoir 22 . The reservoir 22 is formed in the space between the housing 12 and the inner cylinder 16. The opposite end of the inner cylinder 16 is connected to an annular end plate 24 . Annular end plate 24
seals the end of reservoir 22 opposite closed end 14 . The inner circumference of the annular end plate 24 is the piston rod assembly 2
Acts as a bearing for the surface of 6. The piston rod assembly 26 includes a hollow cylindrical strut 28 (branch portion).

The inner end of the strut 28 is connected to the piston mounting stud 3.
0 (post section) and the outer end is closed with mounting studs 3
It is closed at 2. In the vicinity of the piston mounting stud 30, the wall of the cylindrical strut 28 is provided with at least one through hole, such as a hole 34;
The inside of the inner cylinder 16 and the inside of the cylindrical strut 26 are in communication (connected in fluid communication).

The mounting stud 32 is provided with a portion for mounting the piston rod assembly 26 to a vehicle. This portion may be formed by a well-known mounting ring or, as shown in FIG. 1, may be formed by a threaded portion 36 adapted for mounting a lock nut 35. The mounting stud 32 has a cylindrical cavity 38 at its inner end that accommodates a solenoid valve 40.
It also has an axial hole 42 for passing the electrical wiring of the solenoid valve. Details of the solenoid valve 40 will be described below in the passage sb shown in FIG.

Valve seat member 44 connects to the inner end of mounting stud 32.

The piston stud 30 is provided with a land 45 that supports a piston assembly 46. The piston assembly 46 is attached to the piston stud 30 as shown.
It is fixed with a nut 48 screwed onto the end of the 0. The piston stud 30 is provided with a through hole in the axial direction, and the first cylinder portion 50 of the telescoping cylinder assembly 52 is slidably accommodated in the hole. The first cylinder 50 of the telescoping cylinder assembly 52 is connected at one end to the relief valve member 18 and extends therethrough. A fluid passageway 56 is provided at the base of the relief valve member 18 and the interior of the telescoping cylinder assembly 52 is connected to the reservoir 22 via the passageway 56.

A second portion 54 of the telescoping cylinder assembly 52 surrounds and is slidably fitted to the first portion 50f. Second
One end of the portion 54 is connected to the piston stud 30, and the other end is connected to the valve seat member 44.

The piston 46 has a general structure and has a first passage such as a passage 58.
A set of longitudinal passageways is provided. The passageway 58 is open at one end and has a spring-loaded first flap valve 60 at the other end.
is blocked by. Valve 60 allows fluid flow in only one direction, specifically from upper working chamber 62 on one side of piston 46 to lower working chamber 6 on the other side of piston 46.
4 to allow fluid to flow past the piston.

Piston 46 is provided with a second set of longitudinal passages, such as longitudinal passages 66 as shown. The passage 66 is open at the end facing the lower working chamber 64 and closed at the other end by a second seven-lap valve 68 of a spring-loaded type. Valve 68 allows flow in only one direction, and specifically allows fluid to flow from lower working chamber 64 to upper working chamber 62 past piston 46 . As is well known, Shockapunba 10
The compression and repulsion rates of are determined by the diameter of the longitudinal passage 58, 66 and the spring load of the flap valve 60.68.

FIG. 2 shows details of the solenoid valve 40. As shown, the solenoid coil 70 of the solenoid valve 40 is wound around a bobbin 72 surrounding a stator 74. Stator 74 has seven langes 76 that hold one end of bobbin 72. An annular flux plate 78 is biased against the other end of the bobbin T2 by a spring 80 surrounding an armature 82. The other end of the spring 80 engages an outwardly directed 7 flange 84 provided at the other end of the armature 82 to urge the armature toward the poppet 86. A ball 88 is attached to the armature 82 concentrically with an axial through hole 90 (drain port) of the poppet 86. Spring 80 is ball 8
B is biased against the poppet 86 in a direction to close the axial hole 90, and the poppet is biased toward the valve seat 94 side of the valve seat member 44.

The valve seat member 44 is provided with an annular notch 96 surrounding the valve seat 94. The annular notch 96 is connected to the interior of the cylindrical strut 28 through a port 98, and the interior is connected to the working chamber 6 through a through hole 34 provided in the wall of the cylindrical strut 28.
Connected to 2. Annular notch 96 is connected to the opposite side of boppet 86 by a bleed port 100.

The diameter of the bleed port 100 is 900 mm (as described above)
It is small in diameter and size.

In normal use, the shock absorber 10 is installed vertically, the piston rod assembly 26 is attached to a structural member of the vehicle frame, and the other end (tip) of the shock absorber 10 is attached to a wheel. It is fixed to a movable structure of a vehicle via a mounting bracket 102 having mounting holes 104 and 106. The upper and lower working chambers 62, 64 are filled with hydraulic fluid, while the reservoir 2
2 is filled with hydraulic fluid only in a part thereof, and the remaining part is filled with pressurized gas, as is well known.

In the operating state, the piston 46 is normally connected to the inner cylinder 1
60 occupies an intermediate position between the two ends. When the wheel equipped with the shock absorber rides up on the protrusion, a force is applied to the tip of the shock absorber that tends to move the housing 12 and the inner cylinder 16 upward toward the mounting stud 32 attached to the vehicle body frame. This force creates a pressure differential on both sides of the piston 46. When this differential pressure exceeds the required opening force of the spring-loaded flap valve 68, the flap valve 68 opens and hydraulic fluid passes through the passageway 66 into the lower working chamber 6.
4 into the upper working chamber 62, causing housing 12 and inner cylinder 16 to move upwardly relative to piston 46. If the ridge is large, the pressure in the lower working chamber 64 may exceed the required opening pressure of one valve of the two-way relief valve member 18. In this case, hydraulic fluid from the lower working chamber 64 passes through the relief valve member 18 and into the housing 12° and the inner cylinder 1.
6 also flows into the reservoir 22 between the two. In the event of rebound or when the wheel falls into a hole, the shock absorber 10 operates in the opposite manner to that described above, and the passage 58 and flap valve 60 move from the upper working chamber 62 to the lower working chamber 64.
Control the flow of fluid to. The stiffness of the shock absorber 10 in both directions is primarily controlled by the diameter of the passage 58.66 and the spring loading of the flap valve 60.68, respectively.

The stiffness of the shock absorber 10 can be changed by actuating the solenoid valve 40 to leaktically connect the upper working chamber 62 to the reservoir 22 via the telescoping cylinder 52. In FIG. 2, when solenoid coil 70 is de-energized, spring 80 pushes armature 82 toward poppet 86 and ball 8B closes drain port 90. The fluid pressure in the upper working chamber 62 is extended to both sides of the boppet 86 by a bleed port 100 of the poppet valve. Since the pressure in the working chamber 62 is always higher than the pressure in the reservoir 22 (
The poppet 86 is held seated on the valve seat 94 by the differential pressure exerted thereon (this will be discussed below).

When solenoid coil TO is energized, armature 8
2 moves, the ball 88 separates from the poppet 86, and the drain port 90 opens. Because the drain port 90 has a larger diameter than the bleed port 100, the fluid pressure on the armature side of the poppet 86 approaches the pressure in the reservoir 22.

A force due to the pressure of the upper working chamber 62 is applied to the lower surface of the poppet 86 at the current notch 96, and the poppet 96 separates from the valve seat 94. As a result, the upper working chamber 6
A direct fluid communication passageway is formed from the reservoir 22 through the bore 34, the port 98, and the interior of the telescoping cylinder 52.

When a wheel rides up a bump with the solenoid valve not energized, a pressure difference is generated on both sides of the piston 46 as described above, and high pressure fluid flows from the lower working chamber 64 to the upper working chamber 62 through the passage 66. flows to

Since the cross-sectional area of the lower working chamber 64 is larger than that of the upper working chamber 62, the pressure in the upper working chamber 62 increases due to the flow of the high-pressure fluid. The amount of movement of the piston 46 is controlled by the pressure in the upper working chamber 62, since the fluid flow rate in the passageway 66 is proportional to the pressure difference across the piston 46. When the solenoid valve 4o is energized, the upper working chamber 62 is connected to the reservoir 2.
2, and the differential pressure against the piston 46 increases. As a result, the high pressure fluid flow rate in passageway 66 is increased and the compressive stiffness of the shock absorber is decreased.

In the event of a bouncing action or a wheel falling into a hole, a force is created which tends to move the housing and inner cylinder downwardly and away from the mounting studs 32. This force increases the fluid pressure in the upper working chamber 62 above the piston 46. When the solenoid valve 4o is energized, the upper working chamber 62 is connected to the reservoir 2.
2, the movement of the piston 46 is controlled by the relief valve 18.
is primarily controlled by the flow rate of fluid from reservoir 22 to lower working chamber 64 through. The flow rate of fluid from the reservoir 22 to the lower working chamber corresponds to the dimensions of the fluid passageway of the relief valve 18, which passageway dimensions can be selected to reduce the stiffness of the shock absorber by a desired amount upon opening of the solenoid valve.

The stiffness of the single-lenoid shock amplifier is determined by switches and electronic control systems installed on the vehicle control panel.
Can be controlled electrically. In FIG. 3, the control system is provided with a sensor 200 that detects the acceleration or displacement of the shock absorber housing 12 relative to the strut assembly 26 and other structural members of the vehicle frame.

The electronic control unit 202 generates a signal for energizing the solenoid valve 40 of the shock absorber under predetermined conditions. In addition to the sensor 200, the electronic control unit 202 is provided with an input unit connected to a driver-operated manual switch 204. The switch 204 is installed on the control panel or steering wheel of the vehicle, and is connected to the ignition switch 208 of the vehicle.
The vehicle is adapted to receive power from a vehicle power source (battery 206 as shown) via the vehicle.

FIG. 4 shows the structure of the electronic control section 202 in detail. In FIG. 4, the output of sensor 200 is sent to the inputs of comparator 210 and integrator 222. In FIG. In this embodiment, sensor 200 is an accelerometer) and generates a signal whose value is proportional to the acceleration of the shock absorber's outer housing.

Comparator 21G compares the output of sensor 200 with a first reference signal (REF-1) indicating a predetermined vertical acceleration. If the vertical acceleration of the wheel is greater than the predetermined acceleration, the comparator 21G generates a set signal, which triggers the RS flip-flop 214 via the geoagate 212 to enter the set state.

In the set state, the claw 70 claw 214 generates a positive signal at its Q output to activate the solenoid drive circuit 216, thereby energizing the solenoid 40 of the shock absorber 1o. This reduces the stiffness of the shock absorber 10, increases the amount of energy absorbed in the vertical direction of the wheel, and reduces the energy transmitted to the vehicle body frame.

Integrating circuit 222 integrates the output of sensor 200 to generate a speed signal. The speed signal has a polarity indicating the direction of movement of the wheel in the coma plane and a magnitude indicating its speed. When the wheel passes the upper limit of travel in the vertical plane, the magnitude of the speed signal passes through zero and the wheel begins to descend toward the road.
As a result, the velocity signal begins to increase in magnitude with opposite polarity.

The output of the integrating circuit 222 is received at the negative input terminal of the second comparator 224. A second reference signal REF-2 is sent to the positive input of the comparator 224.

When the output of the integrating circuit 222 becomes smaller than the value of the reference signal REF-2, the comparator 224 generates a reset signal, which is passed through the AND gate 220 to the flip 7.
It is sent to the reset terminal of the 0 knob 214.

220a is enabled by switch 204 in the open state, as described below. The reset signal resets the seven-rig flop 214, which deactivates the solenoid drive 216 and de-energizes the solenoid valve 40. As mentioned above, when the solenoid valve 40 is de-energized, the shock absorber 10
The stiffness of increases. When a vertical acceleration larger than the predetermined value set by the first reference signal REF-1 occurs in the wheel, the 7-rig flop 214 is returned to the set state.
Until then, flip-flop 214 remains reset and solenoid valve 40 remains de-energized.

The value of the second reference signal REF-2 is determined by the suspension system of the vehicle and the dynamic characteristics of the vehicle.

For heavy vehicles, a positive value indicating a predetermined vertical speed is used as the reference signal R.
EF-2 so that comparator 224 generates a reset signal so that solenoid valve 40 is de-energized before the wheel reaches the top of its vertical lift range. In a light vehicle, the value of the reference signal REF-2 is set to zero so that the solenoid valve 40 is de-energized at the top of the wheel vertical rise range, or the reference signal is set to a negative value,
It is also possible for the solenoid valve 40 to be de-energized during the lowering movement of the wheel.

The signal from manual switch 204 is sent to the other input of OR gate 212 and to the input of inverter 218. When the manual switch 204 is closed, the 7 lip flop 2
14 is set, and the solenoid drive unit 216 is activated. In response to the closure of manual switch 204, inverter 218 generates a ground or negative output to disable AND gate 220 and prevent the reset signal generated by comparator 224 from resetting flip-flop 214. When manual switch 204 is opened, inverter 218 generates a positive signal to enable antenna controller 22Q.

Note that the integrator circuit 222 and the comparator 224 may be replaced with a timer (not shown) or a single chicot multivibrator triggered by the Q output of the flip-flop 214.

The multi-vibrator and timer generate a reset signal sent to the reset terminal of the flip-flop 214 with a predetermined delay. This reset signal resets the flip-flop 214, de-energizes the solenoid drive section 216, and de-energizes the solenoid valve 40. The duration of the delay is selected such that the stiffness of the shock absorber changes when the wheel is at or near the top of its vertical lift range.

The present invention is not limited to the illustrated embodiment described above, and the variable damping rate shock absorber of the present invention can be embodied in various forms.

[Brief explanation of drawings]

Fig. 1 is a sectional view of the variable damping rate shock absorber, Fig. 2 is an enlarged sectional view showing details of the solenoid valve, Fig. 3 is a block diagram showing the control system of the variable damping rate shock absorber, and Fig. 4 is a block diagram of an electronic control section. i Q * * * * Shock absorber, 12・Salary.・External housing, 16・Production cylinder, 18・
...Valve member, 22...Fluid reservoir, 26...
・Piston rod assembly, 40... solenoid valve,
46...Kyo piston, 52...Telescopic cylinder assembly, 62...Upper working chamber, 64...Lower working chamber, 90...Outlet port, 98...@Yuin Roport. FIG, 2 FIG, 4 1, Indication of the incident Showa et al. 2 in hand Application No. s': bzoq No. 2, Name of '$＄￥, Decay rate Asari L show 7T7゛n-t\゛'3,
person who makes corrections

Claims (15)

[Claims] (1) Connect the closed actuation cylinder (16) to the external housing (
12) to form a fluid reservoir (22), and a piston (46) is disposed within the working cylinder (16) to divide the interior of the working cylinder (16) into an upper working chamber (62) and a lower working chamber (64). ), a connecting means (18) is provided at one end of the working cylinder (16) to connect the lower working chamber (64) to the reservoir (22), and a hollow piston rod (28) is provided at one end to connect the lower working chamber (64) to the reservoir (22).
) is slidably fitted into the other end of the working cylinder, one end of the piston rod is connected to the piston, and the other end extends outside the working cylinder; (16) Inside the telescopic cylinder (50,
52, 54) and one end thereof as a reservoir (22).
a solenoid valve means (40) is disposed inside the hollow piston rod (28), and the other end of the telescoping cylinder is connected to the other end of the telescoping cylinder. an inlet port (98) connected to said solenoid valve means and communicating with said upper working chamber; and said telescoping cylinder (50).
, 52, 54) and an outlet port communicating with the reservoir (22) through the interior of the solenoid valve means (40).
) is configured to switch between an open state and a closed state in response to an electrical input signal, wherein in the open state liquid communication is allowed between the inlet port and the outlet port, and in the closed state, the A variable damping rate shock absorber characterized in that liquid flow is prevented between an inlet port and an outlet port. (2) The connecting means for connecting the lower working chamber (64) to the reservoir (22) is a bidirectional relief valve member (18) disposed at the one end of the lower working chamber, and the relief valve member The variable damping rate shock absorber according to claim 1, further comprising an axial hole (45) into which the one end of the telescoping cylinder fits. (3) providing the hollow piston rod (28) with a cylindrical strut (28), a piston stud (30) and a mounting stud; a wall of the strut at an intermediate position between both ends of the cylindrical strut (28); A through hole (34) is provided in the section, the piston stud (30) is fixedly fitted to one end of the cylindrical strut, and the piston stud is fitted with a through hole (34).
means for attaching a piston (46) to said stud and an axial hole into which said telescoping cylinder is slidably fitted; said mounting stud fixedly fitted to said other end of said cylindrical strut; 2. The variable damping rate shock absorber according to claim 1, wherein said mounting stud is provided with means for mounting said piston rod to a frame of a vehicle. (4) The solenoid valve is formed of a solenoid-driven poppet valve having a poppet member (86) that engages with the valve seat member (44), and the valve seat member is connected to the other end of the telescoping cylinder. , the outlet port (10
0) is provided in a state that communicates with the inside of the telescoping cylinder and is arranged concentrically with the cylinder, and the valve seat member (44)
Claim 3, characterized in that the valve seat (94) surrounds the outlet port, the inlet port being radially offset from the outlet port and communicating with the interior of the tubular strut. The variable damping rate shock absorber described. (5) The telescoping cylinders (50, 52, 54) are provided with an inner cylinder (50) and an outer cylinder (54); one end of the inner cylinder (50) is connected to the relief valve member (1).
8), and the other end is slidably fitted into the axial hole of the piston stud (30) and extends into the cylindrical strut (28); The above inner cylinder (50
) is extended into the interior of the cylindrical strut in a partially surrounded state, and the other end of the outer cylinder is connected to the valve seat (9).
4), and the opposite end thereof is connected to the piston stud (30). (6) The armature (82) elastically biased by the valve seat member (44) and poppet member (84) on the solenoid valve.
), stator member (74), and solenoid coil (70)
and; the valve seat member (44) is connected to the hollow piston rod (28).
) is fixedly disposed at the end opposite to the piston (46) and connected to the other end of the telescoping cylinder (50, 52, 54), and the outlet is connected to the valve seat member (44). The valve seat member (44) includes a valve seat (94) that surrounds the outlet port and an inlet that is radially offset from the outlet port. a port; the poppet member (84) is disposed adjacent to the valve seat member and engageable with the valve seat (94), and the poppet member has an inlet port (98) extending therethrough; ), and an axial spill port (90) communicating with the inside of the telescoping cylinder; the armature (82) being placed on the side opposite to the valve seat member (94); disposed on the poppet member (86);
The armature is engaged with the poppet member that closes the spill port (90) and biases the poppet member toward the valve seat;
) is arranged within the hollow piston rod in a concentric position and spaced a predetermined distance from the armature; the solenoid coil (70) surrounds the stator, and the solenoid coil generates a magnetic field in response to an electrical signal. The variable attenuation rate type according to claim 3, wherein the armature is moved away from the poppet member to generate a force sufficient to open the spill port. shock absorber. (7) providing a cylindrical housing (12) having a closed end, with a closed volume actuating cylinder (16) concentrically disposed within the housing to form a fluid reservoir (22) therebetween; a piston member (46) is disposed within the housing to partition its interior into a lower working chamber (64) and an upper working chamber (62) adjacent to the closed end of the housing; one end of the hollow piston rod (28); The above piston (
46) and extend the other end of the piston rod (28) to the outside of the working cylinder by passing through the end opposite to the end closed by the housing; Attach the end to the bidirectional relief valve member (1
8), the relief valve member forming a bidirectional fluid passage between the lower working chamber and the reservoir; a telescoping cylinder (50, 52, 5) within the working cylinder;
4) is arranged in the axial direction, one end of the cylinder is connected to the relief valve member (18) to communicate with the reservoir (27), and the other end of the telescoping cylinder is connected to the inside of the hollow piston rod. A solenoid valve (40) is arranged on the hollow piston rod (28) and connected to the other end of the telescoping cylinder, and the solenoid valve is provided with an inlet port (40) communicating with the working chamber. 98) and an outlet port (100) communicating with the inside of the telescoping cylinder. (8) The bidirectional relief valve (18) is provided with an axial through hole, and the one end of the telescoping cylinder is arranged to pass through the axial through hole. The variable damping rate shock absorber according to item 7. (9) A cylindrical strut member (28), a piston stud (30), and a mounting stud (32) are provided on the hollow piston rod (28); the piston stud (30) is attached to one end of the cylindrical strut member. fixedly mounted, said piston stud having means for mounting said piston thereon and an axial hole in which said telescoping cylinder is slidably fitted; 8. The variable damping rate shock absorber according to claim 7, wherein the variable damping rate shock absorber is fixedly attached to the other end of the shaped strut member. (10) The solenoid valve (40) is formed of a solenoid-driven poppet valve, and the poppet member (8) is formed of a solenoid-driven poppet valve.
4) and a valve seat member (94) engaged by the poppet member, the member being disposed inside the cylindrical strut member (28) and connected to the other end of the telescoping cylinder; The outlet port (100) is provided in the valve seat member so as to pass through the outlet port (100) in the axial direction and communicate with the inside of the telescoping cylinder;
Claims characterized in that the valve seat (94) surrounds the outlet port (90) and the inlet port (98) is radially offset and communicates with the interior of the strut member. The variable damping rate shock absorber according to item 9. (11) providing the telescoping cylinder (50, 52, 54) with an inner cylinder (50) and an outer cylinder (54);
Connect one end of the inner cylinder (50) to the relief valve member (
18), and the other end is slidably fitted into the axial hole of the piston stud and extends into the cylindrical strut (28);
) is extended into the interior of the cylindrical strut member while partially surrounding the inner cylinder (50), one end of the outer cylinder is attached to the piston stud (30), and the other end is attached to the piston stud (30). 11. The variable damping rate shock absorber according to claim 10, wherein the variable damping rate shock absorber is connected to the outlet port of the valve seat member (44). (12) Valve seat member (44) on the solenoid valve (40)
and a poppet member (86), an elastically biased armature (82), a stator member (74) and a solenoid coil (70); the valve seat member (44) is connected to the hollow piston rod (28).
) is fixedly disposed at the end opposite to the piston (46) and connected to the other end of the telescoping cylinder (50, 52, 54), and the outlet is connected to the valve seat member (44). The valve seat member (44) includes a valve seat (94) that surrounds the outlet port and an inlet that is radially offset from the outlet port. a port (98); the poppet member (86) is disposed adjacent to the valve seat member (94) so as to be engageable with the valve seat member; a predetermined port (100) communicating with the inlet port; and an axial spill port (90) communicating with the interior of the telescoping cylinder; disposed on the poppet member (86) at;
The armature is engaged with the poppet member that closes the spill port (90) and biases the poppet member toward the valve seat;
) is fixedly disposed within the hollow piston rod (32) in a concentric position and spaced a predetermined distance from the armature; the solenoid coil (70) surrounds the stator, and the solenoid coil responds to an electrical signal. to generate a magnetic field, thereby generating a force sufficient to move the armature (82) away from the poppet member (84) and open the spill port (90). A variable damping rate shock absorber according to claim 9. (13) providing an actuating cylinder (16); providing an end member (30) having an axial piston rod hole surrounding one end of said actuating cylinder; and providing a two-way relief valve member (18) at the other end of said actuating cylinder; a reservoir communicating with the two-way relief valve member; a reservoir surrounding the actuating cylinder (16);
) an upper working chamber (62) adjacent to said end member;
and a lower working chamber (64) adjacent to the bidirectional relief valve member.
a hollow piston rod (28) connected to the piston is passed through the piston rod hole to connect the actuating cylinder (1);
a solenoid valve means (40) extending outwardly from the hollow piston rod and having an outlet port and an inlet port (98) communicating with the upper working chamber; 52, 54) are disposed axially within said actuating cylinder (16), one end of said telescoping cylinder being attached to said two-way relief valve member (18) and communicating with said reservoir; A variable damping rate shock absorber, characterized in that its end portion is slidably inserted into the piston member (46) and connected to the outlet port of the solenoid valve means (40). (14) A piston (46) is disposed within the working cylinder (16) so as to be able to freely reciprocate, and the interior thereof is divided into an upper working chamber (62) and a lower working chamber (64), and the piston (46)
a first flow means (58) for allowing fluid to flow from the upper working chamber to the lower working chamber; and a second flow means (58) for allowing fluid to flow from the second working chamber to the first working chamber. Flow means (66) are provided for actuating said first and second flow means in accordance with the direction of movement of said piston; said hollow piston rod (28) is connected to said actuating cylinder for moving said piston; (16) and a hole (34) in said hollow piston rod to allow fluid to flow from said actuating cylinder into said hollow piston rod; 4
0) is movably arranged to control the rate of movement of said piston having an inlet port (98) communicating with the lower hole (34) and an outlet port (100) communicating with the low pressure reservoir (22). . A variable damping rate shock absorber, wherein when the solenoid valve means is in an operating state, fluid flows from the inlet port to the outlet port regardless of movement of the piston. (15) A working cylinder (16) filled with fluid is provided; a piston (46) is reciprocatably disposed within the working cylinder (16) and attached to the hollow piston rod (28); divides the working cylinder into an upper chamber (64) and a lower chamber (62); means are provided for controlling the rate of movement of the piston within the working cylinder (16); direction-responsive first flow means (58) for allowing fluid flow from the upper chamber (62) to the lower chamber when the piston moves in a first direction during relative movement between the piston and the working cylinder; ), allowing fluid to flow from the lower chamber to the upper chamber when the piston moves in a second direction opposite to the first direction in the relative movement between the piston and the working cylinder. and a direction-responsive second flow means (58) for communicating the upper chamber (64) with the inside of the piston rod (28) by providing a hole extending through the piston rod (28). , a solenoid valve means (40) responsive to a control signal is disposed within the piston rod (28) to control the rate of fluid communication from the upper chamber to the low pressure reservoir (22); The means (40) is provided with an inlet through which fluid flows from the hole and an outlet communicating with the reservoir, so that when the solenoid valve means is actuated to allow fluid to flow therethrough, the actuating chamber is A variable damping rate shock absorber, characterized in that the fluid flow communicating with the reservoir and passing through the solenoid always flows in the same direction regardless of the direction of the piston.