JP6391363B2 - Pressure shock absorber - Google Patents

Description

  The present invention relates to a pressure buffering device.

  Suspension devices for vehicles such as automobiles are equipped with a pressure buffering device that uses a damping force generator to appropriately mitigate vibrations transmitted from the road surface to the vehicle body during traveling and improve riding comfort and handling stability. ing. The pressure buffer device includes, for example, a partition member which is movably provided in the cylinder and partitions the cylinder, a rod member connected to the partition member, and oil corresponding to the volume of the rod member as the rod member moves. And a liquid reservoir chamber that compensates for the above, and generates a damping force by providing resistance to the flow of the liquid generated as the partition member moves.

  Further, for example, there is known a pressure buffer provided with a throttle mechanism that is provided on the side of the cylinder and that takes in the liquid in the cylinder and squeezes the liquid flow path to provide resistance and discharge the liquid into the liquid reservoir chamber. Yes. In this throttle mechanism, for example, the flow of oil produced by sliding of a piston in a cylinder is controlled by a pilot-type main valve and a pilot valve which is a pressure control valve to generate a damping force (see, for example, Patent Document 1). ).

JP 2012-72857 A

In the throttling mechanism, when the liquid is discharged into the liquid reservoir chamber while restricting the flow, the liquid level (in the liquid reservoir chamber) undulates, and as a result, gas is mixed into the liquid and bubbles (in the liquid) are generated. May occur. Then, when the liquid containing the bubbles is supplied into the cylinder, for example, when the damping force is generated by a valve or the like in the cylinder, the predetermined damping force is hardly generated until the bubbles disappear, and the predetermined force is not generated. There was a high possibility that the generation of damping force would be delayed.
An object of the present invention is to generate a predetermined damping force in a pressure buffering device including a throttle mechanism that takes in a liquid from a cylinder and discharges the liquid into a liquid storage chamber while constricting the flow.

For this purpose, the present invention is provided between a first cylinder that extends from one side in the axial direction to accommodate the liquid, and the first cylinder that is located radially outside the first cylinder. A second cylinder that forms a liquid reservoir that stores liquid so that a liquid surface is formed on the other side; and a second cylinder that is movable in the axial direction within the first cylinder, A partition member that partitions the liquid into a first liquid chamber and a second liquid chamber; a partition member that is provided on a side of the second cylinder and that restricts a liquid flow path; A throttling mechanism that discharges the liquid that moves as the liquid moves toward the liquid reservoir while passing through the throttling portion, and more than the discharge point of the liquid from the throttling mechanism in the liquid reservoir to the liquid reservoir. Around the first cylinder at the other side Or comprising a limiting mechanism for limiting the flow of liquid in the radial direction, wherein the limiting mechanism, than the discharge portion in the liquid reservoir between the first cylinder and the second cylinder in the other side The pressure buffer device includes a cylindrical partition wall extending in the axial direction, and a communication path that communicates a space partitioned by the partition wall . That is, this configuration has a limiting mechanism that restricts the flow of liquid in the circumferential direction or the radial direction of the first cylinder at a portion on the other side of the discharge location from the throttling mechanism, so that the included bubbles disappear. Or the undulation of the liquid surface is suppressed and bubbles are less likely to be generated.

  According to the present invention, it is possible to generate a predetermined damping force in the pressure buffering device including the throttle mechanism that takes in the liquid from the cylinder and discharges the liquid to the liquid reservoir chamber while restricting the flow.

1 is an overall configuration diagram of a hydraulic shock absorber according to the present embodiment. It is a figure for demonstrating in detail the solenoid valve periphery of this Embodiment. It is a perspective view of the separator which concerns on 1st Embodiment. It is a figure which shows the modification of a separator. It is a figure for demonstrating the flow of the oil in a solenoid valve. It is a perspective view of the separator which concerns on 2nd Embodiment. (A) is a perspective view of the separator which concerns on 3rd Embodiment. (B) is sectional drawing for demonstrating the solenoid valve periphery in detail. It is a figure which shows the modification of the separator which concerns on 2nd Embodiment. (A)-(c) is a figure which shows the modification of the communicating path of the separator which concerns on 3rd Embodiment-the separator which concerns on 1st Embodiment. (A)-(c) is a figure which illustrates a protrusion part. It is a figure for demonstrating in detail the solenoid valve periphery provided with the flow-path restriction | limiting part. It is a figure for demonstrating a flow-path restriction | limiting part.

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
FIG. 1 is an overall configuration diagram of a hydraulic shock absorber 1 according to the present embodiment.
FIG. 2 is a diagram for explaining in detail the periphery of the solenoid valve of the present embodiment.

[Configuration and function of hydraulic shock absorber 1]
As shown in FIG. 1, the hydraulic shock absorber 1 is located on the outer side in the radial direction of the first cylinder 11 that extends from one side of the axial direction to the other and accommodates oil as an example of a liquid. And a second cylinder 12 forming a reservoir chamber R as an example of a liquid reservoir portion in which liquid is accumulated so that a liquid surface is formed on the other side between the first cylinder 11 and an axial direction in the first cylinder 11. And a piston 30 as an example of a partition member that divides the space in the first cylinder 11 into a first liquid chamber Y1 and a second liquid chamber Y2 that store liquid.

  The hydraulic shock absorber 1 is provided on the side of the second cylinder 12 and has a throttle portion that throttles the flow path of the liquid, and the reservoir moves while passing the liquid that moves as the piston 30 moves through the throttle portion. A solenoid valve 50 as an example of a throttle mechanism that discharges toward the chamber R (liquid reservoir), and discharge of liquid from the solenoid valve 50 in the reservoir chamber R (liquid reservoir) to the reservoir chamber R (liquid reservoir) And a separator 80 as an example of a restriction mechanism that restricts the flow of liquid in the circumferential direction or the radial direction of the first cylinder 11 at a portion on the other side of the location.

  The hydraulic shock absorber 1 includes a cylindrical outer cylinder 13 provided between the first cylinder 11 and the second cylinder 12. The first cylinder 11, the second cylinder 12, and the outer cylinder 13 are arranged concentrically (coaxially). The central axis direction of the cylinder of the first cylinder 11 may be simply referred to as “axial direction”. In addition, when the direction in the axial direction of the first cylinder 11 is indicated, the lower part in FIG. Moreover, the term indicating the shape of an object such as “cylindrical” is not limited to the exact shape of a cylinder such as “cylindrical” but also includes the case of an approximate shape such as “substantially cylindrical”.

  Further, the hydraulic shock absorber 1 includes a bottom lid 14 that closes one end of the second cylinder 12 in the axial direction, a rod guide 15 that guides a piston rod 20 described later, oil leakage in the second cylinder 12, An oil seal 16 is provided for preventing foreign matter from entering the second cylinder 12.

  The hydraulic shock absorber 1 also includes a rebound stopper 17 that limits the movement range of the piston rod 20 and a bump stopper cap 18 that is attached to the other end of the second cylinder 12 in the axial direction.

  Further, the hydraulic shock absorber 1 includes an example of a throttle mechanism as shown in FIG. 2, a piston rod 20 that supports the piston 30, a bottom valve 40 provided at one end of the first cylinder 11 in the axial direction. As a solenoid valve 50.

  In this hydraulic shock absorber 1, an oil path (flow) between the first cylinder 11 and the reservoir chamber R between the outer peripheral surface of the cylindrical first cylinder 11 and the inner peripheral surface of the outer cylinder 13. A communication path L is formed.

  A first cylinder through hole 11h is formed on the other end side of the first cylinder 11 and on one side of the rod guide 15 so as to communicate the inside and the outside. The first cylinder through hole 11h Oil flows between the inside of the first cylinder 11 and the communication path L via the.

  As shown in FIG. 2, an outer cylinder through-hole 13h formed so as to communicate between the inside and the outside is formed in the outer cylinder 13 at a position facing the solenoid valve 50. The outer cylinder through-hole 13h is formed in the outer cylinder through-hole 13h. The oil flows from the communication path L to the solenoid valve 50 through the via. And the outer cylinder 13 has the flanged cylindrical joint member 13G which protrudes toward the solenoid valve 50 side around the outer cylinder through-hole 13h. A suction port 52 described later is inserted inside the joint member 13G.

  As shown in FIG. 2, the second cylinder 12 is formed with a second cylinder through-hole 12 h formed so as to communicate between the inside and the outside at a position where the solenoid valve 50 is attached. A solenoid cylinder 50S described later is attached to the outer periphery of the second cylinder 12 and outside the second cylinder through hole 12h.

  As shown in FIG. 1, the bottom cover 14 is attached to one end of the second cylinder 12 and closes one end of the second cylinder 12.

  The rod guide 15 is a member having a substantially cylindrical shape, and is held by the second cylinder 12 on the inner periphery of the second cylinder 12. And the rod guide 15 supports the piston rod 20 so that a movement is possible via the bush etc. which were inserted by the inner hole, for example. The rod guide 15 closes the other end of the first cylinder 11 and the outer cylinder 13 in the axial direction.

  As shown in FIG. 1, the piston rod 20 extends in the axial direction and holds the piston 30 at one end in the axial direction.

  As shown in FIG. 1, the piston 30 includes a piston body 31, a valve 32 provided on the other end side in the axial direction of the piston body 31, and a spring 33.

  The piston 30 is provided in the first cylinder 11 so as to be movable in the axial direction, and the space in the first cylinder 11 is separated from the first liquid chamber Y1 which is a space in which the rod portion 21 of the piston rod 20 is not disposed. It divides into the 2nd liquid chamber Y2 in which the rod part 21 is arrange | positioned.

  As shown in FIG. 1, the bottom valve 40 includes a valve body 41 having a plurality of oil passages formed in the axial direction, and a shaft in a part of the plurality of oil passages formed in the valve body 41. The valve | bulb 42 which plugs up one edge part of a direction and the volt | bolt 40B which fixes these members are provided.

(Solenoid valve 50)
As shown in FIG. 2, the solenoid valve 50 includes a solenoid cylinder 50 </ b> S, a solenoid mechanism 51, a suction port 52, a valve stopper 53, a valve body 54, a spring 55, and a discharge ring 56.

  The solenoid cylinder 50S is a cylindrical member, and is provided so that the opening on the second cylinder 12 side in the center line direction of the cylinder faces the second cylinder through hole 12h of the second cylinder 12. In the present embodiment, the solenoid cylinder 50 </ b> S is provided on the side of the second cylinder 12 so as to face the direction intersecting the axial direction of the first cylinder 11. In the following description, the center line direction of the cylinder of the solenoid cylinder 50S is simply referred to as “crossing direction”. Further, in the crossing direction, the second cylinder 12 side on the left side in FIG. 2 is referred to as “base end side”, and the right solenoid mechanism portion 51 side is referred to as “tip side”.

  The solenoid mechanism 51 includes a coil 511, a housing 511H, a plunger 512, a magnetic body 513, and a fixed core 514.

  The suction port 52 is a member having a generally cylindrical shape. In the present embodiment, the suction port 52 has a proximal end opening 521 and a distal opening 522 having a diameter larger than that of the proximal opening 521. And the base end side opening part 521 is engage | inserted via the sealing member inside the joint member 13G of the outer cylinder 13. As shown in FIG. Further, the front end opening 522 faces the solenoid mechanism 51 with the discharge ring 56 interposed therebetween.

  The valve stopper 53 is a thick-walled cylindrical member having an oil annular channel 53r formed therein. Then, the suction port 52 is attached to the inside of the front end side opening 522.

  The valve body 54 is a member configured such that two cylinders having different diameters are arranged in the intersecting direction, and a proximal-side cylinder portion 54p that is a proximal-side cylinder and a distal-side cylinder that is a distal-side cylinder. Part 54q. The valve body 54 is arranged so that the base end side cylindrical portion 54 p is fitted into the annular flow path 53 r of the valve stopper 53. Further, the valve body 54 moves in the crossing direction by receiving a force from the plunger 512 at the tip side end of the tip side cylindrical portion 54q.

  The spring 55 is a coil spring, and is provided between the valve stopper 53 and the distal end side cylindrical portion 54q of the valve body 54. The spring 55 urges the valve body 54 in the direction in which the distance between the valve stopper 53 and the valve body 54 in the intersecting direction is increased (the direction of the arrow F shown in FIG. 2).

  The discharge ring 56 is a cylindrical member and includes a plurality of circular openings in the circumferential direction on the outer peripheral surface. The discharge ring 56 is positioned around the valve stopper 53, the valve body 54, and the spring 55, and discharges oil that has passed through a throttle portion V described later to the cylinder inner chamber 50R.

  In this embodiment, the oil throttle portion V in the solenoid valve 50 is formed by the annular flow path 53r of the valve stopper 53 and the base end side cylindrical portion 54p of the valve body 54. That is, in the solenoid valve 50 of the present embodiment, the damping force is adjusted by changing the oil flow path by changing the distance of the valve body 54 with respect to the valve stopper 53 by the plunger 512 of the solenoid mechanism portion 51.

(Separator 80 according to the first embodiment)
FIG. 3 is a perspective view of the separator 80 according to the first embodiment.
The separator 80 is a substantially cylindrical member, and has an inner diameter larger than the outer diameter of the outer cylinder 13 and an outer diameter smaller than the inner diameter of the second cylinder 12, and between the outer cylinder 13 and the second cylinder 12. Be placed. That is, the separator 80 is disposed in the reservoir chamber R.

The separator 80 is formed with notches 81 that are notched in a U shape from one end to the other (four in this embodiment) in the circumferential direction. Further, the separator 80 is formed with a communication path 82 (12 in the present embodiment) in the circumferential direction at the other side in the axial direction from the notch 81. In the example shown in FIG. 2, the communication path 82 is a cylindrical through hole whose center line direction is orthogonal to the axial direction.
The communication path 82 may be a through hole whose center line direction is inclined with respect to the axial direction, or a through hole whose diameter decreases gradually from the (radial direction) outer side to the (radial direction) inner side. It may be a hole.

The separator 80 configured as described above is a cylinder extending in the axial direction between the first cylinder 11 and the second cylinder 12 on the other side in the axial direction from the oil discharge point from the solenoid valve 50 to the reservoir chamber R. A partition wall 80a. Further, the cylindrical partition wall 80a of the separator 80 is formed with a communication passage 82 that communicates the space partitioned by the partition wall 80a.
As shown in FIG. 2, the separator 80 is held such that the bottom of the notch 81 (the other end in the axial direction of the notch 81) is caught by the joint member 13G.
Note that the position of the separator 80 in the radial direction may or may not be particularly fixed. For convenience of explanation, the case where the separator 80 is fixed is not mentioned, but various fixing methods can be used. For example, a groove for fitting the separator may be formed in a part of the joint member 13G of the separator 80, or another fixing member may be disposed from the outside in the radial direction of the joint member 13G to fix the position of the separator. Good.

(Modification of separator 80)
FIG. 4 is a view showing a modified example of the separator 80.
The separator 80 may have a plurality (at least three) of protrusions 83 that protrude inward in the radial direction from the inner peripheral surface 80b and extend in the axial direction at equal intervals in the circumferential direction. And it is good to attach the separator 80 so that the some protrusion part 83 provided in the inner peripheral part may contact the outer peripheral surface of the outer cylinder 13. As shown in FIG. Thereby, the radial position of the separator 80 with respect to the outer cylinder 13 and the second cylinder 12 is defined.

[Operation of hydraulic shock absorber 1]
The operation of the hydraulic shock absorber 1 configured as described above will be described.
First, the operation of the hydraulic shock absorber 1 during the compression stroke will be described.
During the compression stroke, when the piston 30 moves to one end side in the axial direction (downward in FIG. 1), the oil in the first liquid chamber Y1 is pushed by the movement of the piston 30, and the first liquid chamber The pressure in Y1 increases.

In the bottom valve 40, the valve 42 remains closed in the oil passage 46, and in the piston 30, the valve 32 that closes the oil passage 31H opens. Then, oil flows from the first liquid chamber Y1 to the second liquid chamber Y2.
Further, oil corresponding to the volume of the piston rod 20 flows out from the first cylinder through hole 11 h, flows through the communication path L, and is supplied to the solenoid valve 50.

FIG. 5 is a view for explaining the oil flow in the solenoid valve 50.
As shown in FIG. 5, in the solenoid valve 50, oil enters from the suction port 52 connected to the communication path L. The oil flowing through the suction port 52 is throttled at a throttle portion V formed between the valve body 54 and the valve stopper 53. At this time, the damping force during the compression stroke in the solenoid valve 50 is obtained. The oil having passed through the throttle portion V is discharged from the discharge ring 56 to the cylinder inner chamber 50R and flows out to the reservoir chamber R.

Next, the operation of the hydraulic shock absorber 1 during the expansion stroke will be described.
When the piston 30 moves to the other end side in the axial direction (upward in FIG. 1), the first liquid chamber Y1 becomes negative pressure. As a result, the oil in the reservoir chamber R opens the valve 42 that closes the oil passage 46 and flows into the first liquid chamber Y1. The oil flow from the reservoir chamber R to the first liquid chamber Y1 is throttled by the valve 42 and the oil passage 46 of the bottom valve 40 to obtain a damping force during the expansion stroke of the hydraulic shock absorber 1.

  Then, the pressure in the second liquid chamber Y2 increased by the movement of the piston 30 toward the other end in the axial direction flows out from the first cylinder through hole 11h, flows through the communication path L, and is supplied to the solenoid valve 50. The The subsequent oil flow in the solenoid valve 50 is as described above with reference to FIG. 5, and the damping force during the extension stroke in the solenoid valve 50 is obtained.

  Further, as described above, in the present embodiment, the separator 80 is provided in the vicinity of the oil discharge location of the solenoid cylinder 50S. Therefore, during the compression stroke and the expansion stroke of the hydraulic shock absorber 1 described above, the solenoid Oil coming out of the valve 50 tends to stay in the notch 81 of the separator 80.

  Further, the oil that has flowed out of the solenoid valve 50 is guided by the notch 81 of the separator 80, moves to one side in the axial direction, and further flows in the reservoir chamber R while being restricted by the separator 80. In other words, the cutout portion 81 of the separator 80 prevents the oil from going to the other side in the axial direction (upward in FIG. 5). Further, since the reservoir chamber R is divided in the radial direction by the separator 80, the oil is directed from the radially outer side to the radially inner side or from the radially inner side to the radially outer side than the separator 80. It is necessary to pass through the communication path 82 formed. Thus, since the flow path of the oil discharged by the solenoid valve 50 is restricted, the force itself toward the other axial side (the upper side in FIG. 1) of the oil is suppressed.

  Further, since the space in the reservoir chamber R is divided by the separator 80, even if the oil surface undulates due to oil discharge or vibration, the size of the wave itself is reduced. As a result, the ripple of the liquid level due to the oil discharged from the solenoid valve 50 is suppressed, and the generation of bubbles in the oil is suppressed. Even if the oil discharged by the solenoid valve 50 contains bubbles, the bubbles disappear because a certain time is required for the oil to reach the oil surface. Therefore, according to the hydraulic shock absorber 1 according to the present embodiment, a delay in the generation of the damping force is suppressed, and a desired damping force can be generated.

  Further, when the above-described protrusion 83 (see FIG. 4) is provided on the inner peripheral portion of the separator 80, the separator 80 itself is held at a predetermined position with respect to the outer cylindrical body 13, and the protrusion The movement of oil in the circumferential direction is restricted by the strip 83.

  In this embodiment, when the separator 80 is held by the joint member 13G, the separator 80 is inserted in the axial direction, and a notch 81 having a shape opened on one side in the axial direction is fitted around the joint member 13G. Assemble. At this time, for example, in the hydraulic shock absorber 1, it is possible to install the separator 80 after assembling all the solenoid valves 50 and the like (see FIG. 2) to the outer cylinder 13 and the second cylinder 12. Thus, in this embodiment, the assembly | attachment property of components can be improved.

<Second Embodiment>
FIG. 6 is a perspective view of a separator 820 according to the second embodiment.
The separator 820 according to the second embodiment is different in that the separator 80 is fixed to the joint member 13G. Below, it demonstrates focusing on a different point.

The separator 820 according to the second embodiment is formed with a through hole 821 penetrating inside and outside. The diameter of the through hole 821 is smaller than the outer diameter of the flange portion of the joint member 13G. The separator 820 is formed with a plurality of communication passages 822 (12 in the present embodiment) in the circumferential direction in the other side in the axial direction from the through hole 821 in the circumferential direction. This is the same as 80 communication paths 82.
And the separator 820 which concerns on 2nd Embodiment is hold | maintained at the joint member 13G because the joint member 13G is press-fit in the through-hole 821, for example.

<Third Embodiment>
FIG. 7A is a perspective view of a separator 830 according to the third embodiment. FIG. 7B is a cross-sectional view for explaining the periphery of the solenoid valve 50 in detail.
The separator 830 according to the third embodiment is different from the separator 80 according to the first embodiment in that a portion having a different thickness is provided. Below, it demonstrates focusing on a different point.

  The separator 830 according to the third embodiment has a protrusion 832 that protrudes in the radial direction of the first cylinder 11, and the protrusion 832 is provided in the vicinity of the solenoid valve 50. That is, the separator 830 has a thin-walled portion 831 that is thinner in the axial direction than the notch 81 (thickness in the radial direction). In the separator 830, a protruding portion 832 is formed at a step provided at the boundary between the thin portion 831 and the partition wall 80a which is a thicker portion than the thin portion 831.

  In the hydraulic shock absorber 1 having the separator 830 according to the third embodiment configured as described above, the oil that has flowed out of the solenoid valve 50 by the protruding portion 832 is on the other side in the axial direction (upward in FIG. 7). And the oil stays in the protruding portion 832. Therefore, by providing the separator 830 according to the third embodiment, it takes a certain time for the oil containing bubbles to pass through to the liquid surface and the like, so that the oil discharged from the solenoid valve 50 contains bubbles. Even if it is, the bubbles disappear.

  Further, since the force itself toward the other side (upper side) of the oil in the axial direction is suppressed, the undulation of the liquid surface is suppressed and the generation of bubbles in the oil is suppressed. And the delay of the damping force generation in the hydraulic shock absorber 1 is suppressed, and the hydraulic shock absorber 1 can generate a predetermined damping force.

In addition, you may apply the thin part 831 and the protrusion part 832 which were shown using Fig.7 (a) and FIG.7 (b) to the separator 820 which concerns on 2nd Embodiment.
FIG. 8 is a view showing a modification of the separator 820 according to the second embodiment.
The separator 820 according to the second embodiment has a thin-walled portion 823 that is thinner around the through-hole 821, and is located at the boundary between the thin-walled portion 823 and the partition wall 80 a that is thicker than the thin-walled portion 823. A protrusion 824 may be formed.

  Also in the hydraulic shock absorber 1 having the separator 820 configured as described above, the protrusion 824 suppresses the oil from the solenoid valve 50 from moving to the other side in the axial direction (upward in FIG. 8). As a result, oil stays in the protruding portion 824. As a result, it takes a certain time for the oil containing air bubbles to pass through the liquid surface and the like, so even if the oil discharged from the solenoid valve 50 contains air bubbles, the air bubbles disappear.

  Further, since the force itself toward the other side (upper side) of the oil in the axial direction is suppressed, the undulation of the liquid surface is suppressed and the generation of bubbles in the oil is suppressed. And the delay of the damping force generation in the hydraulic shock absorber 1 is suppressed, and the hydraulic shock absorber 1 can generate a predetermined damping force.

  In the modification of the separator 830 according to the third embodiment shown by using FIG. 7A and FIG. 7B and the separator 820 according to the second embodiment shown by using FIG. The oil flow in the “outer peripheral part” of the separators 830 and 820 is configured to act on the protruding parts 832 and 824 to reduce the bubbles of the oil, but is not limited to this mode. . That is, between the outer periphery of the outer cylindrical body 13 and the “inner periphery” of the separators 830 and 820, the protrusions 832 and 824 are made to act on the oil flow to prevent the generation of bubbles in the oil. May be.

<Modification of separator communication passage>
Fig.9 (a)-FIG.9 (c) are figures which show the modification of the communicating path 82 of the separator 830 which concerns on the separator 80 which concerns on 1st Embodiment mentioned above-3rd Embodiment.
As shown in FIG. 9A, the flow path communicating between the inside and the outside of the cylindrical separator 80 may be a communication path 82a formed of a through hole extending substantially linearly in the axial direction. Moreover, the shape may be such that not only the axial direction but also the axially extending portion and the circumferentially extending portion are alternated.

Further, as shown in FIG. 9B, the flow path that communicates the inside and the outside of the separator 80 is a through-hole that linearly extends in an inclined direction (the direction of arrow S in FIG. 9B) with respect to the axial direction. The communication path 82b which consists of may be sufficient. In addition, as the communicating path 82b extended in an inclination direction, a wave shape may be sufficient instead of the linear form shown in FIG.9 (b).
Further, as shown in FIG. 9C, the flow path that communicates the inside and the outside of the separator 80 is formed to extend linearly in the axial direction from one end in the axial direction to the other end. The communication path 82c formed by a gap may be used.

  9A to 9C, any one of the communication paths 82a to 82c is formed in the separator 80 according to the first embodiment to the separator 830 according to the third embodiment. An example is shown. However, although not illustrated, any two or more of the communication passages 82a to 82c may be combined to form the separator 80 according to the first embodiment to the separator 830 according to the third embodiment.

<Projection>
The separator 80 according to the first embodiment to the separator 830 according to the third embodiment described above protrudes from the outer peripheral surface toward the second cylinder 12 in the radial direction of the first cylinder 11 (841 to 843). May be provided over the entire circumference of the outer peripheral surface. The protruding portion may have a size that does not reach the inner peripheral surface of the second cylinder 12 in the radial direction of the first cylinder 11. Further, the protruding portion may be provided in the axial direction in the vicinity of the liquid surface, preferably slightly above the liquid surface.

Fig.10 (a)-FIG.10 (c) are figures which illustrate a protrusion part.
The protruding portion 841 illustrated in FIG. 10A is formed so as to have a waveform when viewed from a direction (side) intersecting the center line direction. That is, the projecting portion 841 gradually decreases in opening width toward the one end side from the one end side in the center line direction toward the other end side in the center line direction. A plurality of convex portions 841a formed in the circumferential direction are formed at equal intervals in the circumferential direction. And the bottom part 841c formed in the convex part 841a adjacent to the vertex 841b of the convex part 841a is formed in circular arc shape.

  In the hydraulic shock absorber 1 including the separator 80 provided with the projecting portion 841 configured as described above, the oil discharged from the solenoid valve 50 rises in a limited space in the convex portion 841a of the projecting portion 841. Therefore, the undulation of the liquid surface is suppressed and the generation of bubbles is suppressed.

  Moreover, since the protrusion part 841 is formed over the perimeter of the outer peripheral surface of the separator 80, and the convex part 841a is formed at equal intervals, it is suppressed that the undulation of the liquid level of oil is biased to a specific location. . Therefore, the undulation of the liquid level becomes smaller and the generation of bubbles is suppressed. As a result, the hydraulic shock absorber 1 can obtain a stable damping force.

  The axial position of the protrusion 841 in the separator 80 is set as follows. That is, when this hydraulic shock absorber 1 is installed in, for example, a suspension device (suspension) of an automobile or a motorcycle, an expected standard weight is determined corresponding to the position of the piston 30 when the suspension device is applied. The position of the oil level in the reservoir chamber R may be set to be slightly below the apex 841b of the convex portion 841a.

  The protruding portion 842 illustrated in FIG. 10B has a plurality of cylindrical portions 842a protruding in a cylindrical shape in the axial direction. Each cylindrical portion 842a has a plurality (two in the example of FIG. 10B) of concave portions 842b recessed from the outer peripheral surface at equal intervals in the circumferential direction. In the example of FIG. 10B, the recess 842b is a flat surface formed in a rectangular shape. The concave portions 842b formed in the cylindrical portions 842a adjacent to each other are formed so as to be shifted in the circumferential direction. In the example of FIG. 10B, they are shifted from each other by 90 °.

  In the hydraulic shock absorber 1 including the separator 80 provided with the projecting portion 842 configured as described above, the cylindrical portion 842a prevents oil from moving (rising) to the other side in the axial direction. On the other hand, since the recessed part 842b is formed in the cylindrical part 842a, a part of oil rises by passing through the recessed part 842b. The oil that has passed through the concave portion 842b moves along the circumferential direction while the flow rising by the cylindrical portion 842a located above is suppressed. As the oil moves along the circumferential direction, the flow path of the oil becomes longer, and as a result, bubbles generated in the oil can disappear.

  Here, for example, when the oil that has passed through the recess 842b of the cylindrical portion 842a is restricted from rising by the adjacent cylindrical portion 842a, the oil moves from the recess 842b in opposite directions along the circumferential direction ( FIG. 10B (see arrow). The oils that have moved in the opposite directions along the circumferential direction collide with each other and the flow is canceled out. As a result, the undulation of the liquid level is suppressed and the generation of bubbles is suppressed.

  The protrusion 843 illustrated in FIG. 10C includes a circumferential portion 843a extending in the circumferential direction, and an axial portion 843b extending from the circumferential end of the circumferential portion 843a to the other side (upper side) in the axial direction. A plurality are provided alternately in succession. As a result, as shown in FIG. 10C, the protruding portion 843 has a plurality of circumferential portions 843a in the axial direction and a plurality of axial portions 843b in the axial direction. And as shown in FIG.10 (c), the circumferential direction flow path through which oil flows in the circumferential direction is formed between the circumferential direction parts 843a adjacent to each other in the axial direction, and between the adjacent axial direction parts 843b. Is formed with an axial flow path through which oil flows in the axial direction (see arrows in FIG. 10C). That is, a step-like flow path is formed by the circumferential portion 843a and the axial portion 843b.

  In the hydraulic shock absorber 1 including the separator 80 provided with the projecting portion 843 configured as described above, the oil is prevented from moving (raising) to the other side in the axial direction by the circumferential portion 843a. As the oil moves along the circumferential portion 843a, the oil flow path becomes longer, and as a result, bubbles generated in the oil may disappear. The oil that has moved along the circumferential portion 843a is restricted in flow by colliding with the axial portion 843b. And the oil which collided with the axial part 843b raises along the axial part 843b, and moves to the circumferential direction along the adjacent circumferential part 843a. In this way, the oil moves stepwise along the circumferential direction portion 843a and the axial direction portion 843b, so that the oil flow path becomes longer, the liquid surface undulation is suppressed, and the generation of bubbles is suppressed. .

  In addition, although the protrusion part 841-843 mentioned above is an aspect which protrudes toward the 2nd cylinder 12 from the outer peripheral surface of the separator 830 which concerns on 1st Embodiment-the separator 830 which concerns on 3rd Embodiment, it takes especially. It is not limited to an aspect. In addition to these configurations, the separator 80 according to the first embodiment to the separator 830 according to the third embodiment may protrude from the inner peripheral surface toward the outer cylinder 13. Such a configuration further suppresses the ripple of the oil level and further suppresses the generation of bubbles.

  10A to 10C, any one of the above-described protrusions 841 to 843 is added to the separator 80 according to the first embodiment to the separator 830 according to the third embodiment. An example is shown. However, although not illustrated, any two or more of the protrusions 841 to 843 may be combined and provided in the separator 80 according to the first embodiment to the separator 830 according to the third embodiment.

  Although not shown, at least one of the protrusions 841 to 843 shown in FIGS. 10 (a) to 10 (c) and the communication paths 82a to 82c shown in FIGS. 9 (a) to 9 (c). At least one of the above may be combined and provided in the separator 80 according to the first embodiment to the separator 830 according to the third embodiment.

The solenoid valve 50 described above may include a flow path restriction unit 60 that restricts the direction of oil discharged to the reservoir chamber R.
FIG. 11 is a diagram for explaining in detail the periphery of the solenoid valve 50 provided with the flow path restriction unit 60.
FIG. 12 is a diagram for explaining the flow path restriction unit 60.

  As illustrated in FIG. 12, the flow path restriction unit 60 includes a rectifying member 611 and a skirt member 612.

  As shown in FIG. 12, the rectifying member 611 is a disk-shaped member having an opening 611R and an oil passage 611H.

  The opening 611R has an inner diameter larger than the outer diameter of the proximal end opening 521. Further, the rectifying member 611 is set so that the outer diameter is smaller than the inner diameter of the solenoid cylinder 50S. The rectifying member 611 is provided inside the solenoid cylinder 50 </ b> S while the proximal end side opening 521 of the suction port 52 is passed through the opening 611 </ b> R and is positioned on the outer side in the radial direction of the proximal end side opening 521. The rectifying member 611 is held in the solenoid cylinder 50 </ b> S by being sandwiched between the skirt member 612 and the distal end side opening 522.

  As shown in FIG. 12, the skirt member 612 includes a cylindrical portion 612S and a flange portion 612F provided on the distal end side in the intersecting direction.

  The cylindrical portion 612S has an outer diameter that is substantially equal to the inner diameter of the second cylinder through hole 12h. Further, the cylindrical portion 612S is formed so that the inner diameter is larger than the outer diameter of the joint member 13G. Further, the end portion on the proximal end side of the cylindrical portion 612 </ b> S has a shape along the outer peripheral surface of the outer cylindrical body 13.

  Furthermore, the cylindrical portion 612S includes a cutout portion 612U cut out in a U shape from the end portion toward the flange portion 612F side. In the present embodiment, the skirt member 612 has the notch 612U positioned at the bottom valve 40 in a state where the proximal end of the cylindrical portion 612S is attached along the outer peripheral surface of the outer cylindrical body 13. It arrange | positions so that the edge part of one side may be faced.

  The skirt member 612 is attached so that the flange portion 612F contacts the inner periphery of the solenoid cylinder 50S. The skirt member 612 is set to face the rectifying member 611. Furthermore, the skirt member 612 has a cylindrical portion 612 </ b> S that extends toward the outer peripheral surface of the outer cylindrical body 13 and faces the outer peripheral surface of the outer cylindrical body 13. The skirt member 612 surrounds the joint member 13 </ b> G and the proximal end side opening 521 of the suction port 52.

  When the solenoid valve 50 includes the flow path restriction unit 60, the separators 80, 820, and 830 described above may be supported by the skirt member 612 of the flow path restriction unit 60 instead of being supported by the joint member 13G. .

  In the above-described embodiment, the oil chamber (the first liquid chamber Y1, the second liquid chamber) is formed by a so-called triple pipe structure in which each of the first cylinder 11, the second cylinder 12, and the outer cylinder 13 is formed in a cylindrical shape. Y2), the reservoir chamber R and the communication path L are formed. However, it is not necessarily limited to forming each component by a triple tube structure. For example, in a so-called double pipe structure including the first cylinder 11 and the second cylinder 12, an oil path corresponding to the communication path L of the present embodiment may be separately provided. In this case, a tubular pipe through which oil flows is separately provided in the first cylinder 11, and the liquid chamber in the first cylinder 11 and the suction port 52 of the solenoid valve 50 are connected by this pipe. Also in this case, the separator 80 is attached so as to surround the first cylinder 11 in a state where the separator 80 is supported so as to surround the oil discharge portion from the solenoid valve 50 to the reservoir chamber R in the reservoir chamber R. Thus, bubbles in the oil can be reduced.

DESCRIPTION OF SYMBOLS 1 ... Hydraulic shock absorber, 11 ... 1st cylinder, 12 ... 2nd cylinder, 13 ... Outer cylinder, 20 ... Piston rod, 30 ... Piston, 50 ... Solenoid valve, 80, 820, 830 ... Separator

Claims (4)

A first cylinder that extends from one of the axial directions toward the other and contains a liquid;
A second cylinder that forms a liquid reservoir that is located outside in the radial direction of the first cylinder and in which a liquid is accumulated so that a liquid surface is formed between the first cylinder and the other cylinder;
A partition member provided in the first cylinder so as to be movable in the axial direction, and partitioning a space in the first cylinder into a first liquid chamber and a second liquid chamber for storing a liquid;
The throttle unit is provided at a side portion of the second cylinder and has a throttle unit that throttles a liquid flow path, and the liquid that moves as the partition member moves is directed toward the liquid reservoir while passing through the throttle unit. A throttle mechanism for discharging;
A restriction mechanism that restricts the flow of the liquid in the circumferential direction or the radial direction of the first cylinder in a portion on the other side of the liquid discharge portion from the throttling mechanism in the liquid reservoir to the liquid reservoir;
Equipped with a,
The restriction mechanism has a cylindrical partition extending in the axial direction between the first cylinder and the second cylinder on the other side of the discharge location in the liquid reservoir, and the partition includes A pressure buffering device in which a communication path communicating with a space partitioned by the partition is formed . The throttling mechanism has a surrounding member that surrounds the periphery of the discharge location in the liquid reservoir,
The pressure damper according to claim 1, wherein the limiting mechanism is supported by the enclosure member. The limiting mechanism, pressure damper according to claim 1 or 2 having a protrusion protruding in a radial direction of the first cylinder.   The pressure buffering device according to claim 3, wherein the protrusion is provided on the other side of the discharge location.

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