JP2888054B2 - Variable damping force type shock absorber - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a shock absorber, and more particularly, to a shock absorber having a variable damping force.

[0002]

2. Description of the Related Art As one of shock absorbers of a variable damping force type for vehicles such as automobiles, for example, Japanese Unexamined Utility Model Publication No. 2-6774.
As described in Japanese Patent Publication No. 2 (1993), a cylinder, a piston reciprocatingly fitted to the cylinder and cooperating with the cylinder to define an upper chamber and a lower chamber of the cylinder, and the relative movement of the piston with respect to the cylinder. A damping force generating device that generates a damping force by giving a flow resistance to the flowing working liquid, a bypass passage provided in the piston for connecting and connecting the cylinder upper chamber and the cylinder lower chamber, and a valve provided in the middle of the bypass passage 2. Description of the Related Art A shock absorber including a hole, a spool valve that reciprocally fits in the valve hole and selectively controls the degree of communication of a bypass passage, and an actuator that drives and positions the spool valve is conventionally known.

In such a shock absorber, the position of the spool valve is controlled by an actuator to control the degree of communication of the bypass passage, so that the operation of the cylinder between the cylinder upper chamber and the cylinder lower chamber via the bypass passage is controlled. Since the flow rate of the liquid is controlled, the flow rate of the working liquid passing through the damping force generator is changed, whereby the damping force generated by the damping force generator is variably controlled.

[0004]

In the conventional shock absorber as described above, the spool valve is opened and activated when the hydraulic fluid passes between the spool valve and the wall surface of the valve hole and passes through the bypass passage. In response to the change in the momentum of the liquid in the reciprocating direction of the spool valve, a fluid force acts on the spool valve in the reciprocating direction. The direction and magnitude of the fluid force vary depending on the flow direction of the working liquid and the opening amount of the spool valve, and thus there is a problem that the driving load of the actuator increases and the control of the damping force becomes inaccurate.

[0005] In view of the above-mentioned problems in the conventional variable damping force type shock absorber, the present invention has been improved so that the driving load on the actuator can be reduced and the damping force can be accurately controlled as compared with the related art. It is an object of the present invention to provide a shock absorber of a variable damping force type.

[0006]

According to the present invention, there is provided a cylinder and a first and second cylinder chambers which are reciprocally fitted to the cylinder and cooperate with the cylinder. A piston for defining, a means for generating a damping force by giving a flow resistance to the working liquid flowing with the relative movement of the piston with respect to the cylinder, a valve hole provided in the piston and extending along an axis, a first bypass passage communicating with the first cylinder chamber at the other end communicates with a direction transverse to the valve hole and the front <br/> Kijikusen at one end, the valve hole and the front Kijikusen at one end A second bypass passage communicating with the second cylinder chamber at the other end thereof, and the first and second bypass passages fitted to the valve hole so as to be able to reciprocate along the axis. And a valve for selectively controlling the degree of communication between the valve and the valve. Having an actuator for positioning,
The valve body carries a collision plate protruding in a direction crossing the axis in a portion of the valve hole adjacent to the second bypass passage, and the collision plate is configured to be closer to the valve body than the first bypass passage. This is achieved by a damping force variable shock absorber configured to receive a flow of the working liquid toward the second bypass passage via a space between the valve hole and the wall surface of the valve hole.

[0007]

In the shock absorber constructed as described above, the pressure in the first cylinder chamber is higher than the pressure in the second cylinder chamber, and the hydraulic fluid in the first cylinder chamber is supplied to the first bypass passage. When flowing into the second cylinder chamber via the valve hole and the second bypass passage, when the working liquid passes through the narrowest portion (hereinafter referred to as a variable orifice) between the valve body and the wall surface of the valve hole, Due to the increase in the momentum of the spool valve in the reciprocating direction, a fluid force is applied to the spool valve to urge the spool valve toward the first cylinder chamber.

According to the above construction, the impingement plate carried by the valve element flows the working liquid from the first bypass path to the second bypass path through the space between the valve element and the wall surface of the valve hole. The valve body is urged in the direction of the second cylinder chamber by the dynamic pressure of the working liquid flowing from the first bypass passage to the second bypass passage.
Therefore, when the working liquid flows from the first bypass passage toward the second bypass passage, at least a part of the fluid force acting on the valve body is offset by the dynamic pressure acting on the collision plate, thereby acting on the valve body. The overall force is reduced,
This makes it possible to reduce the driving load on the actuator and accurately position the valve element.

[0009]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram of an embodiment of the present invention.

FIG. 1 is a longitudinal sectional view showing a main part of a first embodiment of a shock absorber according to the present invention configured as a twin tube type shock absorber, and FIG. 2 is a first embodiment shown in FIG. 3 is an enlarged partial longitudinal sectional view showing a main part of the piston of FIG. 1 in a state where the spool valve is in a fully closed position. FIG. 3 shows the spool valve of the first embodiment shown in FIGS. 1 and 2 in a fully open position. FIG. 4 is an enlarged partial longitudinal sectional view.

In FIG. 1, reference numerals 10 and 12 denote inner and outer cylinders extending concentrically along an axis 14, both ends of which are closed by end caps (not shown). Have been. The cylinders 10, 12 and the end cap cooperate with each other to define an annular chamber 16. A piston 18 is arranged in the inner cylinder 10 so as to be able to reciprocate along the axis 14. A piston 18 separates the interior of the inner cylinder 10 into an upper cylinder chamber 20 and a lower cylinder chamber 22, and is integrally connected to the main body and extends along the axis 14 through the end cap at the upper end. And a piston rod 26. The piston body 24 is the nut 2
The piston body 24 is fixed to the distal end portion of the piston rod 26 by a damper 8. The piston body 24 is provided with a damping force generator 30 for an extension stroke having a known structure and a check valve 32 ( see FIG. 2).

Although not shown in FIG. 1, a lower portion of the inner cylinder 10 is provided with a base valve assembly having a well-known structure. The base valve assembly has an extension stroke. A damping force generator for a contraction stroke similar to the damping force generator 30 of the first embodiment is provided. A part of the upper cylinder chamber 20, the lower cylinder chamber 22, and the annular chamber 16 is filled with oil 34 as a working liquid.
The upper part of 6 is filled with high-pressure gas. FIG.
Although not shown, the upper end of the piston rod 26 is connected to the vehicle body as a sprung part, and the outer cylinder 12 or the end cap at the lower end is connected to a suspension member as a unsprung part not shown in the figure. It has become.

As shown in FIG. 2, the piston rod 26 includes a rod member 42 having a hollow hole 40 extending along the axis 14. A valve housing 44 is fixed to the lower end of the rod member 42 by screwing, and an actuator 46 is accommodated in the hollow hole 40.
In the illustrated embodiment, the actuator 46 includes a stepper motor 48 and a ball screw device 50, which functions as a motion converter that converts the rotational motion of the stepper motor into a reciprocating motion of the shaft 52. ing.

The valve housing 44 has a rod portion 44a, which projects below the lower end of the rod member 42 along the axis 14. Nut 28 is rod part 44
It is fixed to the lower end of a by screwing. Rod part 4
4a has a hollow bore 54 extending along the axis 14, the upper portion of which defines a valve bore 58 for reciprocally receiving the spool valve 56 along the axis 14. A stopper 6 is provided between the piston body 24 and the valve housing 44.
0, the spacer 62 and the bypass device 64
It is fixed in a state where it fits.

The bypass device 64 includes a housing 66, a ring member 68, and an end cap 70 that cooperate with each other to define an interior space 72 that extends annularly about axis 14. The housing 66 is provided with a plurality of radially extending grooves 74 communicating with the internal space 72, and is provided with a plurality of passages 76 extending vertically in the end wall thereof. I have. End cap 7
0 has a plurality of passages 78 extending vertically in the figure. Ring member 68 cooperates with housing 66 to define an annular port 80 communicating with groove 74.
The rod portion 44a of the valve housing is provided with a plurality of radial passages 82 communicating with the annular port 80 and an annular port 84 communicating with the passage and opening in the valve hole 68.

The end wall of the housing 66 and the end cap 70 are respectively provided with check valves 86 and 88 in contact with their upper surfaces. The check valve 86 allows only the oil flow from the internal space 72 and the groove 74 to the cylinder upper chamber 20 via the passage 76, and the check valve 88 controls the internal space from the cylinder upper chamber 20 via the passage 78. Only the flow of oil toward 72 and groove 74 is allowed.

As shown in detail in FIG. 3, the spool valve 56 has a hollow 90 extending in its longitudinal direction, the diameter of which is set slightly larger than the diameter of the shaft 52. As a result, the spool valve 56 is loosely fitted to the shaft 52. An annular groove 92 is provided near the lower end of the shaft 52, and a stopper ring 94 is mounted in the annular groove. Stopper ring 9
An annular disc-shaped collision plate 96 which projects radially outward and extends in the circumferential direction perpendicular to the axis 14 is interposed between the lower end of the spool valve 4 and the lower end of the spool valve 56. An annular groove 98 is provided in the shaft 52 above the upper end of the spool valve 56, and a stopper ring 100 is mounted in the annular groove.

A compression coil spring 106 is fitted between the spring seat 102 disposed in contact with the stopper ring 100 and an end face of a counter bore 104 provided at the upper end of the spool valve 56 in a state fitted to the shaft 52. It is armed. The spring force of the compression coil spring 106 is a minimum force sufficient to hold the spool valve in a position in contact with the collision plate 96 which also functions as a washer as shown in the drawing against the fluid force and frictional force acting on the spool valve 56. Value is set to
This allows the spool valve 56 to reciprocate along the shaft as it is reciprocated along the axis 14 by the shaft 52, but to be relatively free to displace relative to the shaft in a direction transverse to the axis 14. ing.

The spool valve 56 cooperates with the valve hole 58 to define an upper chamber 108 and a lower chamber 110 above and below it. These chambers are composed of the counter bore 104, the hollow hole 90 and the shaft 5
2, spool valve, impact plate 92, shaft 5
2. They are connected to each other by a clearance passage between the stopper rings 94. The lower end of the spool valve 56 is tapered so that when the spool valve is in the fully closed position shown in FIG.
When the spool valve is driven upward in the figure from the fully closed position as shown in FIG. 3, the communication between the annular port 84 and the lower chamber 110 is changed. An orifice 112 is defined.

Further, in the illustrated embodiment, the portion of the valve hole 58 below the portion defining the variable orifice 112 in cooperation with the spool valve 56 is enlarged in the figure,
An inclined surface 5 whose diameter gradually increases toward the cylinder lower chamber 22 below the portion defining the orifice in the figure.
8a are provided. The collision plate 96 is provided with the spool valve 5.
6 has an outer diameter slightly larger than the diameter of the lower chamber 11 through the variable orifice 112 through the annular port 84.
It is designed to receive the oil flow to zero.

Thus, passages 76 and 78, internal space 7
2, groove 74, annular port 80, passage 82, annular port 8
Reference numeral 4 denotes a first bypass passage 1 which connects and connects the cylinder upper chamber 20 and the valve hole 58 and communicates with the valve hole in a direction perpendicular to the axis 14.
The hollow hole 54 defines a second bypass passage which connects the cylinder lower chamber 22 and the valve hole 58 and communicates with the valve hole along the axis 14. The degree of communication between the passages is variably controlled by controlling the effective passage sectional area of the variable orifice 112 by the spool valve 56.

In the operation of the illustrated embodiment, in the extension stroke of the piston, the pressure in the cylinder lower chamber 22 becomes lower than the pressure in the cylinder upper chamber 20 and the annular chamber 16 so that the cylinder upper chamber becomes lower. and part of a cyclic chamber oil flows into the cylinder lower chamber, where more flow resistance to oil is provided to the damping force generating equipment 30 for extension stroke provided in the piston to thereby damping force Generated.

Similarly, during the compression stroke of the piston, the pressure in the cylinder lower chamber 22 is increased by the cylinder upper chamber 20 and the annular chamber 16.
When the pressure becomes higher than the internal pressure, a part of the oil in the lower cylinder flows into the upper cylinder and the annular chamber. At that time, the damping force generator for the contraction stroke provided in the base valve assembly converts the oil into oil. On the other hand, a flow resistance is given, thereby generating a damping force.

In both the extension stroke and the contraction stroke of the piston, when the spool valve 56 is in the fully closed position shown in FIG. 2, the bypass passages 114 and 54 are in a state of being shut off from each other. Oil does not flow between the upper cylinder chamber 20 and the lower cylinder chamber 22 via the bypass passage, and the damping force generator is always provided on the piston.
After passing through the damping force generator provided on the base 30 and the base valve assembly, a high damping force is generated by these damping force generators, whereby the shock absorber operates in a so-called hard mode.

On the other hand, when the coil of the step motor 48 is energized and the spool valve 56 is switched to the fully open position or the intermediate position between the fully closed position and the fully open position shown in FIG. 110 and variable orifice 1
12, the bypass passages are in a state of mutual communication, so that a part of the oil in the upper cylinder chamber 20 and the oil in the lower cylinder chamber 22 circulate through the bypass passages, and the damping force generator The shock absorber operates in a so-called soft mode or an intermediate mode between the soft mode and the hard mode depending on the opening position of the spool valve.

In this case, while the oil in the cylinder upper chamber 20 flows through the bypass passage to the cylinder lower chamber 22 during the extension stroke of the piston, the oil passes through the check valve 88, while the oil in the piston compression stroke does not. In this case, the oil in the cylinder lower chamber 22 passes through the check valve 86. However, since the check valve 86 is not biased by a spring, the damping force generated in the compression stroke of the piston is equal to the extension of the piston. Lower than in the journey.

In the extension stroke and the contraction stroke of the piston in a state where the spool valve 56 is opened, the oil passes through the bypass passages 114 and 54 and the variable orifice 112 so that the spool valve 56 has an axis 14. A fluid force acts along. In the illustrated embodiment, such fluid force is represented by a dashed line A in FIG.
Occurs as indicated by. As can be seen from FIG. 4, during the extension stroke of the piston, the displacement of the spool valve in which a relatively strong negative pressure region is generated downstream of the variable orifice 112, that is, on the side of the bypass passage 54 with respect to the variable orifice, is small. , The fluid force acting on the spool valve has a negative value.

According to the illustrated embodiment, during the extension stroke of the piston, the oil flow from the first bypass passage 114 to the lower chamber 110 via the variable orifice 112 collides with the collision plate 96, and the oil flows to the spool valve. When the displacement amount is small, the negative pressure in the negative pressure region generated downstream of the variable orifice is reduced, and when the displacement amount of the spool valve is large, the impingement plate and the spool valve Because 56 is biased downward in the figure, the overall force acting on spool valve 56 is reduced, as shown by solid line B in FIG.

FIG. 5 is an enlarged partial longitudinal sectional view showing the spool valve of the second embodiment of the shock absorber according to the present invention in a fully open position. In FIG. 5, members that are substantially the same as the members shown in FIGS. 1 to 3 are given the same reference numerals as those given in these drawings.

In this embodiment, a portion of the cylindrical outer peripheral surface of the spool valve 56 which faces the annular port 84 has an axis 1
A recess 116 is provided which extends annularly around 4. In the figure of the depression 116, the inclination angle of the upper inclined surface with respect to the axis is set to be larger than the inclination angle of the lower inclined surface.

Therefore, as shown by an arrow 120 in FIG. 5, the oil flows substantially in the same manner as in the first embodiment during the extension stroke of the piston, while the contraction stroke of the piston extends. In FIG. 5, a part of the oil flows in a curved manner in the depression 116 after passing through the variable orifice 112 as indicated by an arrow 122 in FIG. By acting on the surface, the spool valve receives an upward force in the figure.

Therefore, according to the second embodiment, as shown in FIG. 6, the force acting on the spool valve during the extension stroke of the piston is the same as in the first embodiment,
In the compression stroke of the piston, the force acting on the spool valve is reduced as compared with the case of the first embodiment (dashed line B ') as shown by the solid line B.

In each of the above-described embodiments, the collision plate 96 has an annular plate shape, but at least the upper surface of the collision plate is susceptible to the dynamic pressure of the oil flowing from the variable orifice into the lower chamber 110. It may be set to a shape other than a plane. For example, as shown in FIGS. 7 and 8, the upper surface of the collision plate has an inclined surface 96a inclined downward as it goes inward in the radial direction, or the outer peripheral portion of the upper surface of the collision plate in the radial direction is closer to its outer edge. if Re is set to high becomes curved 96b, since the dynamic pressure of the oil acting on the impact plate by the impact plate is subjected to flow efficiently oil is increased, the force acting on the spool valve at a extension stroke of the piston For example, it is further reduced as shown by the imaginary line C in FIGS. 4 and 6, respectively.

According to the illustrated embodiments, the spool valve 56 is loosely fitted to the shaft 52 as described above, and is held at a position where it abuts against the collision plate 96 by the compression coil spring 106. It is urged against the stopper ring 94 along the shaft 52 with a minimal spring force sufficient to do so. Therefore, the spool valve 56 can relatively freely displace relative to the shaft in a direction transverse to the axis 14,
Further, since the compression coil spring 106 does not substantially press the wall of the valve hole 58, the shaft 52
Alternatively, even if these members are assembled in a state where the axis of the spool valve 56 and the axis of the valve hole 58 are shifted from each other, the sliding resistance when the spool valve is reciprocated does not increase. The spool valve can smoothly reciprocate along the valve hole.

According to the illustrated embodiments, the actuator 46 comprises a step motor 48 capable of accurate driving and positioning, and a ball screw device 50 as a motion conversion device for converting the rotational motion of the step motor into a reciprocating motion. Therefore, the spool valve 56 can be driven and positioned more accurately than when a reciprocating actuator is used.

In the above two embodiments, the collision plate 96 is formed as a separate member independent of the spool valve 56. However, the collision plate 96 may be formed integrally with the spool valve 56 as a part thereof. Good.

Although the above two embodiments are configured as twin tube type shock absorbers, the shock absorber according to the present invention may be configured as a so-called mono tube type shock absorber.

The actuator in the shock absorber of the present invention is not limited to the actuator having the structure shown in the illustrated embodiment, but may have any structure as long as the valve can be reciprocated and positioned. May be.

Although the present invention has been described in detail with reference to specific embodiments, the present invention is not limited to such embodiments, and various other embodiments may be made within the scope of the present invention. The possibilities will be clear to the skilled person.

[0040]

As is apparent from the above description, according to the present invention, the collision plate carried on the valve element passes through the first bypass passage between the valve element and the wall surface of the valve hole so that the second collision plate passes through the second bypass path. The valve body is configured to receive the flow of the working liquid toward the bypass passage, and the valve body is applied in the direction of the second cylinder chamber by the dynamic pressure of the working liquid from the first bypass passage toward the second bypass passage. When the working fluid flows from the first bypass passage toward the second bypass passage, at least a part of the fluid force acting on the valve body is offset by the dynamic pressure acting on the impingement plate. Since the overall force acting on the body is reduced, the driving load on the actuator can be reduced, whereby the actuator can be reduced in size and energy consumption can be reduced, and the valve body can be driven smoothly and accurately positioned. It is possible to improve the responsiveness of precisely controlling the damping force control the damping force of the shock absorber by determining.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a main part of a first embodiment of a shock absorber according to the present invention configured as a twin tube type shock absorber.

FIG. 2 is an enlarged partial longitudinal sectional view showing a main part of the piston of the first embodiment shown in FIG. 1 in a state where a spool valve is in a fully closed position.

FIG. 3 is an enlarged partial longitudinal sectional view showing the spool valve of the first embodiment shown in FIGS. 1 and 2 in a fully open position.

FIG. 4 is a graph showing the relationship between the amount of displacement of the spool valve and the axial force acting on the spool valve in the first embodiment.

FIG. 5 is an enlarged partial longitudinal sectional view showing a spool valve of a second embodiment of the shock absorber according to the present invention in a fully open position.

FIG. 6 is a graph showing the relationship between the amount of displacement of the spool valve and the axial force acting on the spool valve in the second embodiment.

FIG. 7 is an enlarged partial longitudinal sectional view showing another embodiment of the collision plate.

FIG. 8 is an enlarged partial longitudinal sectional view showing still another embodiment of the collision plate.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... Inner cylinder 12 ... Outer cylinder 18 ... Piston 20 ... Cylinder upper chamber 22 ... Cylinder lower chamber 24 ... Piston main body 30 ... Damping force generator 34 ... Oil 46 ... Actuator 48 ... Step motor 50 ... Ball screw device 54 ... No. Second bypass passage 56 ... Spool valve 58 ... Valve hole 96 ... Collision plate 112 ... Variable orifice 114 ... First bypass passage

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. ⁶ , DB name) F16F 9/00-9/58 B60G 13/08 F16K 1/38 F16K 3/314

Claims (1)

(57) [Claims] 1. A cylinder, a piston reciprocally fitted to the cylinder and cooperating with the cylinder to define first and second cylinder chambers, and a relative movement of the piston with respect to the cylinder. Means for giving a flow resistance to the flowing working liquid to generate a damping force, a valve hole provided in the piston and extending along an axis, and one end crossing the valve hole and the axis at one end. a first bypass passage communicating with the first cylinder chamber at the other end communicates with the direction, and the second cylinder chamber at the other end communicates along said valve hole and before Kijiku line at one end A second bypass passage communicating with the valve, a valve body fitted in the valve hole so as to reciprocate along the axis, and selectively controlling the degree of communication between the first and second bypass passages; and the valve body. And an actuator for reciprocating and positioning the
The valve body carries a collision plate protruding in a direction crossing the axis in a portion of the valve hole adjacent to the second bypass passage, and the collision plate is configured to be closer to the valve body than the first bypass passage. A variable damping force type shock absorber configured to receive a flow of a working liquid toward the second bypass passage through a space between the valve hole and the wall surface of the valve hole.