JP2017180606A - Valve mechanism, attenuation force generation device and shock absorber - Google Patents

Abstract

PROBLEM TO BE SOLVED: To generate an attenuation force surely and with high accuracy.SOLUTION: A control valve part 60 includes: a valve seat member 50 having a valve seat formed radially outside of an opening on one end of a central flow passage 106 of an oil; a drive valve 61 provided movably in a direction approaching/separating from the valve seat; a plurality of pieces of valve bodies 72 provided between the valve seat and the drive valve 61, and having openings 77 in which the oil circulates; a solenoid actuator which moves the drive valve 61 in a direction approaching the valve seat, and which makes a gap flow passage between an inner peripheral part of the valve body 72 and the valve seat variable by elastically deforming the valve body 72 closest to the drive vale 61, out of the plurality of pieces of valve bodies 72, in the direction in which the inner peripheral part approaches the valve seat with respect to the outer peripheral part of the valve body 72; and a valve rotation restricting part 80 for restricting the relative rotation of the plurality of valve bodies 72 in the circumferential direction, in a state where the openings 77 of the plurality of valve bodies 72 are communicated with each other.SELECTED DRAWING: Figure 7

Description

  The present invention relates to a valve mechanism that adjusts a damping force generated by controlling the flow of a fluid, a damping force generator, and a shock absorber.

  For example, a shock absorber is provided between a wheel and a vehicle body of a motorcycle to reduce vibrations and shocks input from the wheel side. As a shock absorber, a fluid is sealed, a wheel and a cylinder connected to one of the wheels, a piston slidably provided in the cylinder, a piston connected to the piston and extending to the outside of the cylinder, and the wheel and the vehicle body. There is known a configuration including a piston rod connected to the other of the first and second, and a damping force generating section that generates a damping force by the flow of fluid when the piston slides in the cylinder.

  Among such shock absorbers, there is a so-called electronic control type in which the damping force generated is made variable in accordance with the traveling state or the like by controlling the flow of fluid in the damping force generating unit during traveling.

Patent Document 1 includes a valve seat provided in a fluid flow path and a valve body (valve part) provided so as to be movable forward and backward with respect to the valve seat, and is formed in a gap between the valve seat and the valve body. In other words, a configuration is disclosed in which the flow of the fluid is controlled by making the dimension of the channel opening through which the fluid flows variable. In this configuration, the valve body is supported by a leaf spring provided in the housing. The leaf spring is elastically deformed according to the magnitude of the pressure of the fluid that presses the valve body, the dimension of the flow path opening between the valve body and the valve seat changes, and the generated damping force changes.
The valve body is provided at the tip of the solenoid movable element, and is driven in a direction in which the valve body is brought into contact with and separated from the valve seat by an electromagnetic force generated between the solenoid stator and the solenoid movable element. By controlling the current value applied to the solenoid stator and displacing the position of the valve body with respect to the valve seat, the dimension of the flow path opening is variable.

Special table 2011-52562 gazette

In the shock absorber, the dimensional accuracy of the flow path opening is particularly important in the region where the piston operates at a low speed.
On the other hand, in the configuration disclosed in Patent Document 1, the positional accuracy of the valve body provided at the tip of the solenoid movable element with respect to the valve seat is the accuracy of the mounting position of the solenoid stator with respect to the housing, and the valve seat in the housing. It depends on machining accuracy such as position accuracy.

In addition, if the flow of fluid is obstructed for any reason other than the site where the original damping force is generated, a predetermined damping force may not be obtained.
An object of the present invention made there is to provide a valve mechanism, a damping force generator, and a shock absorber that can reliably and highly accurately generate a damping force.

The present invention employs the following means in order to solve the above problems.
A valve mechanism according to the present invention includes a housing having a valve seat formed on the radially outer side of an opening at one end of a fluid flow path, and a drive valve provided so as to be movable toward and away from the valve seat. And a plurality of valve bodies provided between the valve seat and the drive valve and having openings through which the fluid flows, and the drive valve is moved in a direction approaching the valve seat, and a plurality of sheets The valve body closest to the drive valve is elastically deformed in the direction in which the inner peripheral portion approaches the valve seat with respect to the outer peripheral portion of the valve body. Drive valve moving mechanism that makes the gap between the valve seat and the valve seat variable, and the openings of the plurality of valve bodies in communication with each other in the circumferential direction. And a rotation restricting portion that restricts general rotation.

  According to the valve mechanism, the damping force generator, and the shock absorber according to the present invention, the damping force can be generated reliably and with high accuracy.

It is sectional drawing which shows the whole structure of the buffer which concerns on embodiment of this invention. It is a top view which shows the damper case provided in the said buffer. It is sectional drawing which shows the damping force generator provided in the said damper case. It is an expanded sectional view which shows the structure of the control valve part of a damping force generator. It is a top view of the valve body which constitutes the 1st valve and the 2nd valve. It is a perspective view which shows the structure of the rotation restraint part provided in the valve body. It is a perspective developed view which shows the structure of a control valve part. It is sectional drawing which shows the state which displaced the drive valve to the valve-seat side with a solenoid actuator, pressed the 2nd valve, made it bend-deforms, and made the opening dimension of the aperture | diaphragm | squeeze part small. It is sectional drawing which shows the state which the adjustment valve part and the drive valve displaced in the direction which leaves | separates from a valve seat by the pressure of oil in a pressure side process. It is sectional drawing which shows the state which displaced in the direction which leaves | separates a drive valve from a valve seat by the pressure of oil in the extending side stroke. It is a top view which shows the modification of the said rotation restraint part. It is a perspective view which shows the other modification of the above or a transfer restraint part. It is sectional drawing which shows the modification of the said damping-force generator. It is sectional drawing which shows the modification of the said damping-force generator. It is sectional drawing which shows the modification of the said damping-force generator.

DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for implementing a valve mechanism, a damping force generation device, and a shock absorber according to the present invention will be described with reference to the accompanying drawings. However, the present invention is not limited only to these embodiments.
FIG. 1 is a cross-sectional view showing the overall configuration of a shock absorber according to an embodiment of the present invention.
As shown in FIG. 1, the shock absorber 10 is provided, for example, between a vehicle body of a motorcycle and a rear wheel support portion that supports a rear wheel, and cushions shocks and vibrations input from the rear wheel. In the following description, the shock absorber 10 extends in the vertical direction, the vehicle body side mounting portion 18 provided at the upper end portion thereof is connected to the vehicle body side, and the axle side mounting member 20 provided at the lower end portion is provided on the rear wheel side. Connected. However, the present invention does not exclude the case where the shock absorber 10 is provided so as to extend in the lateral direction (substantially horizontal direction), for example.

  The shock absorber 10 includes a cylinder 11, a piston 12, a piston rod 13, a reservoir 30, a damping force generator 40, and a spring (not shown).

  The cylinder 11 includes an inner cylinder 14 and an outer cylinder 15 that form a concentric double pipe. A damper case 16 provided with a vehicle body side mounting portion 18 is disposed on the upper end side of the shock absorber 10. The damper case 16 is provided with a cylindrical cylinder holding portion 17 extending toward the cylinder 11 side. The upper and lower ends of the outer cylinder 15 and the inner cylinder 14 are inserted and held in the cylinder holding portion 17.

  The inner diameter of the outer cylinder 15 of the cylinder 11 is larger than the outer diameter of the inner cylinder 14 by a certain dimension. Thereby, a cylindrical flow path 101 is formed between the outer cylinder 15 and the inner cylinder 14.

The outer cylinder 15 is formed so as to protrude below a predetermined dimension from the lower end portion 14 b of the inner cylinder 14. An annular rod guide 23 that supports the piston rod 13 so as to be slidable in the central axis direction is provided inside the lower end portion 15 b of the outer cylinder 15. The lower end portion 14b of the inner cylinder 14 abuts on the upper surface of the rod guide 23, whereby the lower end of the flow path 101 is closed.
In addition, the rod guide 23 is provided with a rebound rubber 24 on the upper side for absorbing an impact when the piston 12 collides.

  The piston 12 is provided inside the inner cylinder 14 of the cylinder 11 so as to be slidable along the central axis direction of the inner cylinder 14. By this piston 12, the inner space of the inner cylinder 14 of the cylinder 11 is partitioned into a piston side oil chamber S1 formed on the damper case 16 side and a rod side oil chamber S2 formed on the piston rod 13 side. .

  An oil hole 102 that opens to the piston-side oil chamber S1 is formed in the damper case 16 at a position facing the upper end opening of the inner cylinder 14. The oil hole 102 communicates with a first oil chamber S11 (see FIG. 3) of the damping force generator 40 described later.

  A plurality of oil holes 103 are formed in the lower end portion 14 b of the inner cylinder 14, and the rod side oil chamber S <b> 2 and the flow path 101 communicate with each other through these oil holes 103.

Furthermore, a plurality of oil holes 104 are formed in the outer cylinder 15 at a portion facing the cylinder holding portion 17 at the upper end portion of the flow path 101. Through these oil holes 104, the piston-side oil chamber S1 and the flow path 101 communicate with each other.
In the damper case 16, a flow path 105 communicating with a third oil chamber S <b> 13 (see FIG. 3) of the damping force generator 40 described later is formed at a position facing the oil hole 104.

  The piston rod 13 is fixed to the piston 12 by a nut 19. The piston rod 13 extends along the central axis direction of the inner cylinder 14, passes through the rod guide 23, and projects outward from the cylinder 11. An axle side mounting member 20 is provided at the lower end 13 b of the piston rod 13. A bump rubber 22 is provided on the cylinder 11 side of the axle-side mounting member 20 so as to pass through the piston rod 13 to prevent the shock absorber 10 from bottoming.

"Reservoir"
FIG. 2 is a plan view showing a damper case provided in the shock absorber.
As shown in FIG. 2, the reservoir 30 is formed in the damper case 16 and has, for example, a cylindrical shape and includes a bag-like bladder 31 therein. The bladder 31 is formed into a bag shape by an elastic body such as rubber, and can expand and contract. The bladder 31 is filled with a gas such as air. In the reservoir 30, the space outside the bladder 31 is an oil reservoir chamber S <b> 3, and communicates with a second oil chamber S <b> 12 (see FIG. 3) of the damping force generator 40 described later via the communication path 107. ing.

  The piston-side oil chamber S1, the rod-side oil chamber S2, the flow path 101 between the inner cylinder 14 and the outer cylinder 15, the oil reservoir chamber S3 in the reservoir 30, and the later-described damping force generation, as described above. The device 40 is filled with oil which is a fluid.

"Damping force generator"
FIG. 3 is a cross-sectional view showing a damping force generator provided in the damper case.
The damping force generator 40 is provided in a bottomed cylindrical damper holding portion 27 formed in the damper case 16. The damping force generating device 40 has a cylindrical shape as a whole, and includes a cartridge case 41, a main damper (damping force generating mechanism) 42, a valve seat member (housing) 50, and a control valve portion (valve mechanism) 60. Mainly prepared.

The damping force generator 40 is provided with a cylindrical cartridge case 41 on the first end 40a side. A male screw portion 41 n is formed on the outer peripheral surface of the cartridge case 41. The damping force generation device 40 is detachably held by the damper holding portion 27 by screwing the male screw portion 41n of the cartridge case 41 into the female screw portion 27n formed on the inner peripheral surface of the damper holding portion 27.
In the following description, in the damping force generation device 40, the side where the cartridge case 41 is provided is the first end 40a, the opposite side is the second end 40b, and the direction connecting the first end 40a and the second end 40b. Is the direction of the central axis C.

  The main damper 42 is provided on the second end 40 b side of the damping force generator 40 so as to be exposed from the cartridge case 41. The main damper 42 includes a valve stopper 39, a pressure side outlet check valve 43, an extension side valve seat member 44, an extension side damping valve 45, an intermediate portion from the second end 40b side to the first end 40a side of the damping force generator 40. The member 46, the pressure side damping valve 47, the pressure side valve seat member 48, and the extension side outlet check valve 49 are sequentially arranged. These valve stopper 39, pressure side outlet check valve 43, extension side valve seat member 44, extension side damping valve 45, intermediate member 46, pressure side damping valve 47, pressure side valve seat member 48, and extension side outlet check valve 49 are: Each is formed in an annular shape.

A plurality of extension side inlet oil passages 44t and pressure side outlet oil passages 44c are alternately formed in the extension side valve seat member 44 along the circumferential direction. The extension side inlet oil passage 44t and the pressure side outlet oil passage 44c are formed through the extension side valve seat member 44 in the direction of the central axis C, respectively.
The extension-side inlet oil passage 44t opens to the second end 40b side of the extension-side valve seat member 44. The extension side damping valve 45 is provided so as to close the outlet on the first end 40a side of the extension side inlet oil passage 44t. The expansion side damping valve 45 is configured by laminating a plurality of disk valves 45v.
The pressure side outlet oil passage 44 c is open to the first end 40 a side of the expansion side valve seat member 44. The pressure side outlet check valve 43 includes a disk valve 43v and is provided so as to close the outlet on the second end 40b side of the pressure side outlet oil passage 44c.

A plurality of pressure side inlet oil passages 48c and extension side outlet oil passages 48t are alternately formed in the pressure side valve seat member 48 along the circumferential direction. The pressure side inlet oil passage 48c and the extension side outlet oil passage 48t are formed so as to penetrate the pressure side valve seat member 48 in the direction of the central axis C, respectively.
The pressure side inlet oil passage 48 c opens to the first end 40 a side of the pressure side valve seat member 48. The pressure side damping valve 47 is provided so as to close the outlet on the second end 40b side of the pressure side inlet oil passage 48c. The compression side damping valve 47 is configured by stacking a plurality of disk valves 47v.
The extension-side outlet oil passage 48t opens to the second end 40b side of the compression-side valve seat member 48. The extension side outlet check valve 49 includes a disk valve 49v and is provided so as to close the outlet on the first end 40a side of the extension side outlet oil passage 48t.

The expansion side damping valve 45 and the compression side attenuation valve 47 normally block the flow of oil by closing the compression side inlet oil passage 48c and the extension side inlet oil passage 44t. The expansion side damping valve 45 and the compression side attenuation valve 47 are bent and deformed according to the pressure of the oil passing through the compression side inlet oil passage 48c and the extension side inlet oil passage 44t, and the compression side inlet oil passage 48c and the extension side inlet oil passage 44t. When oil passes through the gap, a damping force is generated. The expansion-side damping valve 45 and the compression-side damping valve 47 adjust the generated damping force by adjusting the number of disk valves 45v and 47v.
The pressure-side outlet check valve 43 and the extension-side outlet check valve 49 normally block the pressure-side outlet oil passage 44c and the extension-side outlet oil passage 48t to block the oil flow, and the pressure-side outlet oil passage 44c and the extension-side outlet It bends and deforms according to the pressure of the oil passing through the oil passage 48t, and distributes the oil.

The valve seat member 50 has a small diameter portion 51 and a large diameter portion 52.
The small diameter portion 51 is formed on the second end 40 b side in the valve seat member 50. The small-diameter portion 51 extends along the direction of the central axis C of the damping force generator 40, and has an annular valve stopper 39, a pressure side outlet check valve 43, an extension side valve seat member 44, an extension side damping valve 45, an intermediate member 46, The pressure side damping valve 47, the pressure side valve seat member 48, and the extension side outlet check valve 49 are inserted through openings formed in the central part. The outer diameter of the small diameter portion 51 is an annular valve stopper 39, a pressure side outlet check valve 43, an extension side valve seat member 44, an extension side damping valve 45, an intermediate member 46, a pressure side damping valve 47, a pressure side valve seat member 48, and It is formed with the same size as the diameter of the opening formed at the center of the extension side outlet check valve 49. The movement of the valve stopper 39 arranged closest to the second end 40b side in the direction from the small diameter portion 51 to the second end 40b side is restricted by a stopper ring 39s provided on the outer peripheral surface of the small diameter portion 51. .

  The large diameter portion 52 has an outer diameter larger than that of the small diameter portion 51 and is continuously formed on the first end 40 a side of the small diameter portion 51. An orthogonal surface 53 orthogonal to the central axis C direction is formed between the large diameter portion 52 and the small diameter portion 51. The extension side outlet check valve 49 abuts on the orthogonal surface 53 and is restricted from moving toward the large diameter portion 52.

FIG. 4 is an enlarged cross-sectional view showing the configuration of the control valve portion of the damping force generator.
As shown in FIG. 4, the large diameter portion 52 is formed with a recess 54 that is recessed toward the small diameter portion 51. A boss portion 55 protruding from the bottom surface 54 b of the concave portion 54 is formed at the center of the concave portion 54 of the large diameter portion 52.
The large-diameter portion 52 is formed with a cylindrical portion 52t on the first end 40a side and further expanding on the outer peripheral side and extending to the first end 40a (upper side of FIG. 4, see FIG. 3) side. .

  The large diameter portion 52 is formed with flow passage holes 56 and 57 that penetrate the inside and outside of the large diameter portion 52. The channel hole 56 is formed at a position facing the outer peripheral surfaces of the first valve 71A and the second valve 71B of the control valve unit 60 described later. The channel hole 57 is formed at a position near the bottom surface 54 b of the recess 54 with respect to the channel hole 56.

  As shown in FIG. 4, the valve seat member 50 is formed with a central flow path 106 that communicates the distal end portion 51 s of the small diameter portion 51 on the second end 40 b side and the boss portion 55 of the large diameter portion 52. .

In such a valve seat member 50, the cylindrical portion 52t and a part of the large diameter portion 52 on the first end 40a side are inserted into the cartridge case 41, the large diameter portion 52 on the second end 40b side, and the small diameter portion A main damper 42 held by 51 protrudes outward from the cartridge case 41.
The main damper 42 protruding from the cartridge case 41 to the second end 40b side and the large-diameter portion 52 of the valve seat member 50 are inserted and arranged inside the bottomed cylindrical damper holding portion 27.

Returning to FIG. 3, the expansion side valve seat member 44 and the pressure side valve seat member 48 of the main damper 42 are provided with annular seal rings 44 s and 48 s on the outer peripheral surface thereof. In a state where the main damper 42 is accommodated in the damper holding portion 27, the seal rings 44 s and 48 s abut against the inner peripheral surface of the damper holding portion 27, so that between the damper holding portion 27 and the main damper 42, A first oil chamber S11, a second oil chamber S12, and a third oil chamber S13 are formed.
The first oil chamber S11 is formed closer to the first end 40a than the seal ring 48s of the pressure side valve seat member 48. The second oil chamber S <b> 12 is formed between the seal ring 44 s of the expansion side valve seat member 44 and the seal ring 48 s of the compression side valve seat member 48. The third oil chamber S <b> 13 is formed between the bottom portion on the second end 40 b side of the damper case 16 and the seal ring 44 s of the expansion side valve seat member 44.

The tip 51s of the small diameter portion 51 of the valve seat member 50 is disposed in the third oil chamber S13 of the damper case 16, and the third oil chamber S13 and the central flow path 106 formed in the small diameter portion 51 communicate with each other. Yes.
In addition, a communication passage 107 communicating with the oil reservoir chamber S3 in the reservoir 30 is formed in the damper case 16 at a position facing the second oil chamber S12 between the compression side valve seat member 48 and the expansion side valve seat member 44. Has been.

  The control valve unit 60 adjusts the driving valve 61, the solenoid actuator (driving valve moving mechanism) 62 that drives the driving valve 61, the valve seat 63, and the flow path opening between the driving valve 61 and the valve seat 63. An adjustment valve unit 70.

  The drive valve 61 is cylindrical and slides along the direction of the central axis C of the damping force generator 40 into an annular valve holder (holder member) 64 fitted inside the cylindrical portion 52t of the valve seat member 50. It is provided as possible. In the drive valve 61, as shown in FIG. 4, a tapered portion 61t whose outer diameter gradually decreases toward the valve seat member 50 side is formed at the tip portion facing the valve seat member 50. Further, the drive valve 61 is formed with a through hole 61h communicating with the central axis C direction. Further, the drive valve 61 is formed with a rod accommodating portion 61s that is recessed toward the distal end side at the rear end portion on the first end 40a side (see FIG. 3).

  As shown in FIG. 3, the solenoid actuator 62 is provided in the cartridge case 41. The solenoid actuator 62 includes two cores 65A and 65B, a coil 66, a rod 67, and a plunger 68.

The two cores 65A and 65B have a bottomed cylindrical shape having recesses 65c and 65d. The two cores 65A and 65B are provided with the concave portions 65c and 65d facing each other, whereby a plunger chamber 69 continuous in the direction of the central axis C is formed.
The coil 66 has a cylindrical shape and is disposed on the outer peripheral side of the plunger chamber 69.

The rod 67 extends along the central axis C direction, and is guided by the guide bush 65g provided in one core 65A and the guide bush 65h provided in a recess formed in the other core 65B. Is slidably held along.
The rod 67 is formed with a through hole 67h penetrating in the central axis C direction.

The distal end portion of the rod 67 on the second end 40 b side is inserted into a rod accommodating portion 61 s provided in the drive valve 61. The outer diameter of the rod 67 is smaller than the inner diameter of the rod housing portion 61 s, thereby forming a cylindrical gap 61 a between the rod 67 and the rod housing portion 61 s. A communication hole (not shown) that communicates the inside of the through hole 67h and the gap 61a is formed at the tip of the rod 67.
Further, a back pressure chamber 65r that extends outward in the radial direction of the rod 67 is formed between the core 65A and the valve holder 64. The back pressure chamber 65r communicates with the gap 61a, and further communicates with the inside of the through hole 67h of the rod 67 through a communication hole (not shown).

  In such a solenoid actuator 62, the rod 67 moves forward and backward in the direction of the central axis C by adjusting the electromagnetic force generated by the coil 66 by increasing / decreasing the current applied to the coil 66. The position of the drive valve 61 can be adjusted in the direction of the central axis C by moving the rod 67 back and forth.

  As shown in FIG. 4, the valve seat 63 is formed on the outer peripheral side of the opening of the central flow path 106 opened in the boss portion 55 of the valve seat member 50 so as to be orthogonal to the central axis C.

  The adjustment valve unit 70 includes a first valve 71A, a second valve 71B, and a spacer 73.

Each of the first valve 71A and the second valve 71B includes a plate-like valve body 72.
FIG. 5 is a plan view of a valve body constituting the first valve and the second valve.
As shown in FIG. 5, each valve body 72 includes an annular outer frame 74, an annular inner frame 75 concentrically provided on the inner peripheral side of the outer frame 74, and an inner side of the inner frame 75. And a formed center hole (through hole) 76. Further, in the first valve 71A and the second valve 71B, a plurality of openings 77 are formed between the outer frame 74 and the inner frame 75 at intervals in the circumferential direction. On both sides in the circumferential direction of the opening 77, spokes 72S that connect the outer frame 74 and the inner frame 75 are formed between the openings 77 and 77 adjacent to each other in the circumferential direction.
In the example shown in FIG. 5, each valve body 72 is formed with a total of three openings 77 at intervals in the circumferential direction around the central axis C.

  Returning to FIG. 4, the first valve 71 </ b> A is disposed on the valve seat 63 side and is configured to be able to contact and separate from the valve seat 63. The second valve 71B is arranged on the drive valve 61 side opposite to the valve seat 63 via the first valve 71A.

  The spacer 73 has a predetermined thickness in the direction of the central axis C, and is sandwiched between the outer frame 74 of the first valve 71A and the outer frame 74 of the second valve 71B. The spacer 73 is annular and has the same outer diameter as the outer diameters of the first valve 71A and the second valve 71B. The spacer 73 forms a gap flow path 110 having an opening size that is the same as the thickness of the spacer 73 in the direction of the central axis C between the first valve 71A and the second valve 71B. Here, it is preferable that the thickness of the spacer 73 in the direction of the central axis C is set to a dimension that can exhibit a damping function as the throttle portion S as will be described later when oil flows through the gap flow path 110.

FIG. 6 is a perspective view showing a configuration of a rotation restraining portion provided in the valve body. FIG. 7 is a perspective developed view showing the configuration of the control valve portion.
As shown in FIG. 6, in the adjusting valve unit 70, the two valve bodies 72 forming the first valve 71A and the second valve 71B are relatively rotated around the central axis C (see FIG. 4). In order to prevent displacement in the circumferential direction, a valve rotation restricting portion (rotation restricting portion) 80 is provided. In the present embodiment, the valve rotation restricting portion 80 includes a locking claw (protrusion) 81 provided on the valve holder 64.
As shown in FIG. 7, a plurality of locking claws 81 are integrally formed on the valve holder 64 at an inner side in the radial direction with respect to the end face 64 f at intervals along the circumferential direction. Each locking claw 81 extends from the valve holder 64 toward the second end 40b, and is formed in a tapered shape such that its tip end gradually becomes thinner toward the second end 40b.

In this embodiment, a total of six such locking claws 81 are formed at substantially equal intervals in the circumferential direction. Two of these locking claws 81 are inserted into each opening 77 of the valve body 72 constituting the first valve 71A and the second valve 71B. Here, as shown in FIG. 6, inside each opening 77, the two locking claws 81 abut against both circumferential edges 77 e and 77 e of the opening 77 with a gap in the circumferential direction. Thereby, the movement to the circumferential direction of each valve | bulb 72 is restrained.
Further, in each opening 77, between the engaging claws 81, 81 arranged at both ends in the circumferential direction, both sides of the valve body 72 are communicated to form a flow passage 82 serving as an oil passage. Yes.

Returning to FIG. 4, in a state where a current is applied to the coil 66 of the solenoid actuator 62, the drive valve 61 has the taper portion 61 t inserted into the center hole 76 of the second valve 71 </ b> B, and further the taper portion 61 t is the second taper portion 61 t. It abuts against the inner peripheral edge 75e of the inner frame 75 of the valve 71B. Accordingly, the first valve 71A, the spacer 73, and the second valve 71B are urged toward the valve seat 63, and the first valve 71A hits the valve seat 63.
In this state, in the first valve 71 </ b> A and the second valve 71 </ b> B, the inner peripheral edge 75 e of the inner frame 75 projects from the valve seat 63 toward the central axis C (in the radial direction).

  In addition, a gap is formed between the second valve 71B and the end surface 64f of the valve holder 64 on the second end 40b side in a state where the first valve 71A is in contact with the valve seat 63.

Further, the control valve unit 60 is provided with a cylindrical sleeve 78 and a coil spring (biasing member) 79.
The sleeve 78 is accommodated in the concave portion 54 on the outer peripheral side of the boss portion 55 of the valve seat member 50, and is provided so as to be movable along the central axis C direction from the bottom surface 54 b of the concave portion 54 toward the valve holder 64 side. . An end 78a on the first end 40a side of the sleeve 78 abuts against the outer frame 74 of the first valve 71A. Further, a ring-shaped rib 78r is formed on the inner side of the end portion 78a of the sleeve 78 so as to project toward the central axis C side (inner side in the radial direction).

  The coil spring 79 is provided inside the sleeve 78. The coil spring 79 is provided in a compressed state between the bottom surface 54 b of the recess 54 of the valve seat member 50 and the rib 78 r of the sleeve 78. In the state where current is applied to the coil 66 of the solenoid actuator 62, the coil spring 79 has a biasing force toward the second end 40b side of the drive valve 61 such that the second valve 71B, the spacer 73, the first valve 71A, By acting through the sleeve 78, the compressed state is maintained.

  In the shock absorber 10 configured as described above, when the rear wheel moves up and down following the unevenness of the road surface while the motorcycle is running, the piston rod 13 is centered with respect to the cylinder 11 as the rear wheel moves up and down. It moves in and out along the direction of the axis C. Accordingly, the piston 12 in the cylinder 11 slides along the central axis C direction integrally with the piston rod 13.

(Pressure side operation)
In the pressure side stroke in which the piston 12 moves toward the vehicle body in the cylinder 11, the oil in the piston side oil chamber S <b> 1 is compressed by the piston 12. Then, the oil in the piston side oil chamber S <b> 1 is sent from the oil hole 102 formed in the damper case 16 to the first oil chamber S <b> 11 formed in the damper holding portion 27. As shown by the arrow C1 in FIG. 3, the oil fed into the first oil chamber S11 passes through the pressure side inlet oil passage 48c formed in the pressure side valve seat member 48 of the main damper 42 and is provided on the outlet side thereof. The compression side damping valve 47 is pushed open and flows into the second oil chamber S12. At this time, the pressure side damping valve 47 is pushed open, and the oil passes through a gap formed between the outlet of the pressure side inlet oil passage 48c and the pressure side damping valve 47, thereby generating a damping force.

  A part of the oil flowing into the second oil chamber S12 is formed in the damper case 16 as shown by an arrow C2 in FIG. 3 in order to compensate for the volume change of the piston rod 13 in the cylinder 11 as the piston 12 moves. Through the communication path 107, the oil flows into the oil reservoir S3. Further, as shown by an arrow C3 in FIG. 3, the remaining oil flowing into the second oil chamber S12 flows into the pressure side outlet oil passage 44c of the expansion side valve seat member 44, and pushes the pressure side outlet check valve 43 to open the second side. It flows into the three oil chamber S13.

  As indicated by an arrow C4 in FIG. 3, the oil that has flowed into the third oil chamber S13 flows into the central flow path 106 from the distal end portion of the small diameter portion 51 of the valve seat member 50 and heads toward the control valve portion 60.

  As shown by an arrow C5 in FIG. 4, in the control valve portion 60, the oil flows between the inner peripheral edge 75e of the inner frame 75 of the first valve 71A and the inner peripheral edge 75e of the inner frame 75 of the second valve 71B. It passes through the gap flow passage 110 formed therebetween, and flows out into the first oil chamber S11 on the outer peripheral side of the valve seat member 50 through the flow passage hole 56 formed in the large diameter portion 52 of the valve seat member 50.

  At this time, the opening dimension of the gap flow path 110 formed between the inner peripheral edge 75e of the inner frame 75 of the first valve 71A and the inner peripheral edge 75e of the inner frame 75 of the second valve 71B is the first valve 71A. The throttle portion S is defined by the thickness of the spacer 73 provided between the second valve 71 </ b> B and has a sufficiently small channel cross-sectional area as compared with the central channel 106. As the oil passes through the throttle portion S, a damping force is generated.

FIG. 8 is a cross-sectional view showing a state in which the driving valve is displaced toward the valve seat by the solenoid actuator, the second valve is pressed to bend and deform, and the aperture size of the throttle portion is reduced.
As shown in FIG. 8, when the current applied to the coil 66 of the solenoid actuator 62 is increased to cause the drive valve 61 to protrude toward the valve seat 63 (second end 40b), the spoke 72S of the second valve 71B is Centering on the outer frame 74 side, the inner frame 75 side bends and deforms in a direction approaching the first valve 71A. Then, the opening size of the gap flow path 110 formed between the inner peripheral edge 75e of the inner frame 75 of the first valve 71A and the inner peripheral edge 75e of the inner frame 75 of the second valve 71B is the plate thickness of the spacer 73. It becomes smaller than the dimension. Thereby, the opening area of the throttle part S can be reduced, and the damping force generated when the oil passes through the gap channel 110 (the throttle part S) can be increased.
In this manner, the control valve unit 60 is generated by controlling the amount of deformation of the second valve 71B by the solenoid actuator 62. The damping force can be adjusted.

FIG. 9 is a cross-sectional view illustrating a state in which the adjustment valve unit and the drive valve are displaced in a direction away from the valve seat due to the oil pressure in the pressure side stroke.
As shown in FIG. 9, when the wheel is suddenly displaced in the vertical direction due to unevenness of the road surface and the piston 12 is displaced at high speed in the cylinder 11, it passes through the central flow path 106 of the valve seat member 50 via the main damper 42. Due to the pressure of the oil flow C6 that has reached the control valve 60, the portion of the inner frame 75 of the first valve 71A that protrudes from the valve seat 63 toward the central axis C (inward in the radial direction) becomes the pressure receiving portion P1, and is driven. It is pressed to the valve 61 side (first end 40a side). If the oil pressure at this time is large, the first valve 71A, the spacer 73, the second valve 71B, and the drive valve 61 are pressed against the biasing force generated by the solenoid actuator 62, and the first end It is displaced to the 40a side. At this time, since oil flows to the drive valve 61 side of the first valve 71A, the valve seat 63 side and the drive valve 61 side of the first valve 71A have the same pressure. Thereby, the first valve 71A is lifted together with the second valve 71B and the drive valve 61 without being bent. As a result, in addition to the throttle portion S formed by the gap flow path 110 between the first valve 71A and the second valve 71B, the throttle portion S is also formed between the inner frame 75 of the first valve 71A and the valve seat 63. Is done. When oil passes through these throttle parts S, S, a damping force is exhibited.
The oil that has passed through these clearance channels 110 flows into the first oil chamber S11 through the channel hole 56 formed in the large diameter portion 52 of the valve seat member 50. The channel hole 57 has an inner diameter smaller than that of the channel hole 56, and oil does not flow through the channel hole 57 during normal operation.

(Extension process)
In the extension side stroke in which the piston 12 moves to the wheel side in the cylinder 11 by the vertical movement of the wheel, the oil in the rod side oil chamber S2 is compressed by the piston 12. Then, the oil in the rod side oil chamber S <b> 2 passes through the oil hole 103 formed in the lower end portion of the inner cylinder 14 to the cylindrical flow path 101 formed between the inner cylinder 14 and the outer cylinder 15. Flows in. The oil flowing through the flow path 101 passes from the oil hole 104 formed in the upper end portion of the outer cylinder 15 through the flow path 105 formed in the damper case 16 to the third oil chamber S13 of the damping force generator 40. It is sent.

  As shown by an arrow T1 in FIG. 3, the oil sent into the third oil chamber S13 flows into the extension side inlet oil passage 44t of the extension side valve seat member 44, and the extension side damping valve 45 provided on the outlet side thereof. A damping force is generated by pushing open.

  The oil that has passed through the gap formed between the extension side inlet oil passage 44t and the extension side damping valve 45 flows into the second oil chamber S12. Further, as shown by an arrow T2 in FIG. 3, in order to compensate for the volume change of the piston rod 13 in the cylinder 11 due to the movement of the piston 12, the oil reservoir chamber S3 passes through the communication passage 107 formed in the damper case 16. Oil flows into the second oil chamber S12.

  The oil flowing into the second oil chamber S12 passes through the extension side outlet oil passage 48t of the compression side valve seat member 48 and pushes and opens the extension side outlet check valve 49 as shown by an arrow T3 in FIG. It flows into S11.

  As shown by an arrow T4 in FIG. 4, the oil in the first oil chamber S11 flows from the flow path hole 56 formed in the large diameter portion 52 of the valve seat member 50 to the inside of the large diameter portion 52 of the valve seat member 50. Flow into. Further, the oil flows from the flow passage 82 of the opening 77 formed in the second valve 71B to the clearance passage 110 (throttle portion S) between the inner frame 75 of the first valve 71A and the inner frame 75 of the second valve 71B. ) And flows into the central flow path 106 formed in the valve seat member 50. At this time, the damping force is generated by the oil passing through the gap flow path 110 between the first valve 71A and the second valve 71B.

  Also in this case, the opening size of the gap flow path 110 between the inner peripheral edge 75e of the inner frame 75 of the first valve 71A and the inner peripheral edge 75e of the inner frame 75 of the second valve 71B is the deflection of the second valve 71B. The amount of deformation is controlled by controlling the solenoid actuator 62. As a result, as shown in FIG. 8, when the current applied to the coil 66 of the solenoid actuator 62 is increased to cause the drive valve 61 to protrude toward the valve seat 63 (second end 40b), the spoke of the second valve 71B 72S is bent and deformed in the direction in which the inner frame 75 side approaches the first valve 71A with the outer frame 74 side as the center. Then, the opening size of the gap flow path 110 formed between the inner peripheral edge 75e of the inner frame 75 of the first valve 71A and the inner peripheral edge 75e of the inner frame 75 of the second valve 71B is the plate thickness of the spacer 73. It becomes smaller than the dimension. Thereby, the opening area of the throttle part S can be reduced, and the damping force generated when the oil passes through the gap channel 110 (the throttle part S) can be increased as shown by the arrow T4 in FIG.

FIG. 10 is a cross-sectional view showing a state in which the drive valve is displaced in a direction away from the valve seat due to oil pressure in the pressure-extended side stroke.
By the way, when the wheel is suddenly displaced by unevenness of the road surface and the piston 12 is displaced at high speed in the cylinder 11, the flow formed in the large-diameter portion 52 of the valve seat member 50 as shown by an arrow T7 in FIG. A part of the oil that has flowed into the large diameter portion 52 from the passage hole 56 strongly collides with the tapered portion 61 t of the drive valve 61.
Here, a back pressure is applied to the drive valve 61 to press the drive valve 61 toward the valve seat 63 from the first end 40a side. This is because oil flows into the back pressure chamber 65r through the through hole 61h formed in the drive valve 61 and the through hole 67h of the rod 67. This back pressure cancels most of the pressure generated by the oil colliding with the tapered portion 61t of the drive valve 61. As a result, in the taper portion 61t of the drive valve 61, a portion on the outer peripheral side of the outer diameter of the rod 67 in the drive valve 61 and on the outer peripheral side of the inner peripheral edge portion 75e of the inner frame 75 of the second valve 71B is the pressure receiving portion P2. Thus, the drive valve 61 is pressed away from the valve seat 63 by the pressure acting on the pressure receiving portion P2.
When the oil pressure acting on the pressure receiving part P2 exceeds the urging force of the solenoid actuator 62, the drive valve 61 moves in a direction away from the second valve 71B toward the first end 40a. Then, in addition to the throttle portion S formed by the gap flow path 110 between the inner frame 75 of the first valve 71A and the inner frame 75 of the second valve 71B, the tapered portion 61t of the drive valve 61 and the inner frame 75 of the second valve 71B. The narrowed portion S is also formed between the inner peripheral edge portion 75e of the first and second inner peripheral portions 75e. That is, the flow path area of the throttle part S formed in the control valve part 60 increases. The oil that exhibits a damping force when the oil passes through the throttle portions S, S passes through the throttle portions S, S and passes through the central flow path 106 of the valve seat member 50 to the third oil chamber S13. Flows in.

In the control valve unit 60, the damping force generation device 40, and the shock absorber 10 in the present embodiment, the control valve unit 60 includes a valve seat 63 that is formed on the radially outer side of the opening at one end of the oil central flow path 106. The valve seat member 50, the drive valve 61 provided so as to be movable toward and away from the valve seat 63, and the opening 77 provided between the valve seat 63 and the drive valve 61 and through which oil flows. And the drive valve 61 is moved in a direction approaching the valve seat 63, and the valve body 72 closest to the drive valve 61 among the plurality of valve bodies 72 is moved to the valve body 72. A solenoid actuator 62 that makes the gap flow path 110 between the inner peripheral portion of the valve body 72 and the valve seat 63 variable by elastically deforming the inner peripheral portion toward the valve seat 63 with respect to the outer peripheral portion; The openings 77 of the plurality of valve bodies 72 In a state where the communication includes a valve rotation restraining part 80 for restraining the relative rotation in the circumferential direction of the plurality of the valve body 72, a.
According to such a configuration, the second valve 71B, which is the valve body 72 closest to the drive valve 61 among the plurality of valve bodies 72, is moved by the solenoid actuator 62 to the valve seat 63 side. Is elastically deformed, the gap passage 110 between the inner periphery of the valve body 72 and the valve seat 63 is narrowed. The oil generates a damping force by passing through the gap channel 110 (throttle portion S). Furthermore, the damping force generated in the gap flow path 110 can be adjusted by adjusting the elastic deformation amount of the valve body 72 by the drive valve 61. Here, the opening size of the gap flow path 110 (throttle portion S) is determined by the distance between the valve body 72 closest to the drive valve 61, that is, the second valve 71B, and the valve seat 63. If the valve body 72 is provided with high accuracy by positioning the valve body 72 with the spacer 73 as in the above embodiment, it is not affected by the processing accuracy of other various parts. Therefore, the damping force can be generated with high accuracy in the control valve unit 60.

  In such a control valve portion 60, the oil passes through the gap passage 110 between the valve body 72 and the valve seat 63, between the central passage 106 radially inward of the gap passage 110 and the radially outer side. Circulate. The oil flows through the openings 77 of the plurality of valve bodies 72 on the radially outer side with respect to the gap flow path 110. If the openings 77 of the plurality of valve bodies 72 are displaced from each other in the circumferential direction, the openings 77 are blocked or throttled by the other valve bodies 72, and the oil flow passage cross-sectional area cannot be secured. Sometimes. On the other hand, the valve rotation restricting portion 80 restricts the relative rotation of the plurality of valve bodies 72, thereby maintaining the state where the openings 77 of the plurality of valve bodies 72 are in communication with each other. Can be secured. Therefore, in the control valve unit 60, the oil flow path is not carelessly restricted except for the gap flow path 110, and the damping force can be reliably exhibited.

Further, the control valve unit 60 includes a valve holder 64 that movably holds the drive valve 61 on the drive valve 61 side with respect to the valve body 72, and the valve rotation restraint unit 80 is provided on the valve body 72 side from the valve holder 64. And a locking claw 81 formed so as to engage with the plurality of valve bodies 72.
According to such a configuration, by engaging the locking claws 81 formed on the valve holder 64 with the plurality of valve bodies 72, the plurality of valve bodies 72 are communicated with the openings 77. Can be restrained.

Further, the locking claws 81 are inserted into the openings 77 of the plurality of valve bodies 72, and portions other than the portions where the locking claws 81 are inserted in the openings 77 serve as the oil flow passages 82.
According to such a configuration, by inserting the locking claw 81 into the opening 77, the plurality of valve bodies 72 can be restrained in a state where the openings 77 are in communication with each other. Further, in the opening 77, since the portion other than the portion where the locking claw 81 is inserted becomes the oil flow passage 82, the opening 77 has the function of engaging the locking claw 81 and the oil flow passage 82. It has the function to form. Therefore, it is not necessary to separately form an engaged portion for engaging the locking claw 81 in addition to the opening 77, and the valve body 72 can be easily manufactured as a simple shape.

In addition, the control valve unit 60 further includes a spacer 73 that is sandwiched between the plurality of valve bodies 72 and that defines the gap flow path 110 between the plurality of valve bodies 72. The damping force can be exerted by the oil passing through the gap channel 110 formed between the valve bodies 72. The spacer 73 can be formed by punching a plate material by pressing or the like, and the plate thickness accuracy can be easily increased. Thereby, since the dimension of the gap flow path 110 between the plurality of valve bodies 72 can be accurately defined by the spacer 73, the damping force generated when the oil passes through the gap flow path 110 is adjusted with high accuracy. can do. Moreover, the spacer 73 can adjust the clearance dimension of the aperture | diaphragm | squeeze part S easily by varying the plate | board thickness and the number of sheets.

  The valve body 72 includes an annular outer frame 74 and an inner frame 75, an opening 77 formed between the outer frame 74 and the inner frame 75, and a center hole 76 formed inside the inner frame 75. ,have. By configuring the second valve 71B with such a valve body 72, pressing the inner frame 75 with the driving valve 61 allows the inner peripheral portion (inner frame) to be opposed to the outer peripheral portion (outer frame 74) of the valve body 72. 75) can be elastically deformed so as to be in contact with and away from the valve seat 63. The adjustment valve portion 70 is a gap between the radially inner side of the inner frame 75 of the valve body 72 and the opening 77 on the radially outer side of the inner frame 75 that form the first valve 71A and the second valve 71B, respectively. By causing the oil to flow through the flow path 110, a damping force can be generated in the gap flow path 110. That is, the adjustment valve unit 70 of the control valve unit 60 can be configured by using a plurality of such valve bodies 72.

Further, the damping force generation device 40 includes the control valve unit 60 as described above and a main damper 42 that is provided independently of the control valve unit 60 and generates a damping force due to oil circulation. Thereby, oil distribute | circulates to the control valve part 60 and the main damper 42, and can each exhibit a damping force by the distribution | circulation of oil.
In addition, according to such a configuration, by providing the control valve portion 60 as described above, it is possible to maintain the state where the openings 77 of the plurality of valve bodies 72 communicate with each other and secure an oil flow path. it can. Therefore, in the control valve unit 60, the oil flow path is not carelessly restricted except for the gap flow path 110, and the damping force can be reliably exhibited.

Further, the shock absorber 10 is connected to the control valve portion 60 as described above, a cylinder 11 in which oil is sealed, a piston 12 slidably fitted in the cylinder 11, and a cylinder 11 connected to the piston 12. Of the piston rod 13 extended outside, the oil reservoir chamber S3 for compensating the amount of oil corresponding to the volume of entry of the piston rod 13 when the piston rod 13 enters the cylinder 11, and the piston 12 in the cylinder 11 The oil generated by the sliding flows into the control valve unit 60 to generate a damping force, and the oil that has passed through the control valve unit 60 can flow through the oil reservoir S3.
In such a shock absorber 10, oil can also flow through the oil reservoir chamber S <b> 3 in the main damper 42. Specifically, the main damper 42 includes a compression side damping valve 47 that generates a damping force during the compression side stroke, a compression side outlet check valve 43 provided downstream of the compression side damping valve 47 during the compression side stroke, and a damping force during the extension side stroke. An oil reservoir chamber is formed between the extension side damping valve 45 to be generated, the extension side outlet check valve 49 provided on the downstream side of the extension side damping valve 45 during the extension side stroke, and the pressure side damping valve 47 and the pressure side outlet check valve 43. S3 is communicated, and between the expansion side damping valve 45 and the expansion side outlet check valve 49 is communicated with the oil reservoir S3.
According to such a configuration, the amount of oil in the cylinder 11 is compensated by the exchange with the oil reservoir chamber S3 according to the volume of the piston rod 13 entering the cylinder 11. Since the pressure in the rod side oil chamber S2 in the cylinder 11 is almost dependent only on the pressure in the oil reservoir chamber S3, the pressure in the rod side oil chamber S2 does not increase immediately at the transition from the compression stroke to the extension stroke. It is possible to avoid the phenomenon of so-called “damping force reduction” in which the damping force is not normally generated.
In addition, according to such a configuration, by providing the control valve portion 60 as described above, it is possible to maintain the state where the openings 77 of the plurality of valve bodies 72 communicate with each other and secure an oil flow path. it can. Therefore, in the control valve unit 60, the oil flow path is not carelessly restricted except for the gap flow path 110, and the damping force can be reliably exhibited.

(Modification of the embodiment)
In the above embodiment, the rotation of the two locking claws 81, 81 is restricted by inserting the valve body 72 into each opening 77, but this is not restrictive.
For example, as shown in FIG. 11, with respect to the plurality of openings 77, a locking claw 81 that abuts the circumferential edge 77 f of the opening 77 on one side in the circumferential direction, and an opening 77 on the other circumferential side. And a locking claw 81 that abuts against the circumferential edge 77g.

  In addition to this, if the circumferential length of the opening 77 is larger than the circumferential length of the locking claw 81, the two locking claws 81, 81 can restrain rotation in two circumferential directions. For example, the arrangement of the locking claws 81 is not questioned at all.

In the above embodiment, by inserting the locking claw 81 into the opening 77, the relative displacement in the circumferential direction of the plurality of valve bodies 72 is restrained, and the locking claw 81 is formed in the opening 77. The portion other than the inserted portion is used as the oil flow passage 82, but is not limited thereto.
The valve body 72 may be provided with a hole for engaging the locking claw 81 and an oil flow passage separately.

Furthermore, in the said embodiment, although the latching claw 81 as the valve rotation restraint part 80 was formed in the valve holder 64, it is not restricted to this.
For example, as shown in FIG. 12, one valve body 72A of the plurality of valve bodies 72 is provided with a protrusion 85 projecting to the other valve body 72B, and is formed on the other valve body 72B. You may make it engage with the joint hole 86. FIG.
According to such a configuration, the projection 85 formed on one valve body 72A of the plurality of valve bodies 72 is engaged with the engagement holes 86 of the other valve body 72B, thereby allowing the plurality of the plurality. The single valve body 72 can be restrained in a state where the openings 77 communicate with each other.

  Further, a concave portion that is recessed radially inward is provided on the radially outer side of the outer frame 74 of the plurality of valve bodies 72, and for example, a convex portion provided on the valve seat member 50 side is engaged with the concave portion. Good.

  In addition to this, for example, the sleeve 78 and the valve seat 63 may be provided with protrusions that extend toward the valve holder 64 and engage with the plurality of valve bodies 72.

  For the purpose of securing an oil flow path between the openings 77 of the plurality of valve bodies 72, the relative relationship between the plurality of valve bodies 72 is maintained in a state where the openings 77 are in communication with each other. If the rotation is constrained, the plurality of valve bodies 72 do not necessarily need to be constrained to rotate in the circumferential direction with respect to the valve seat member 50.

In each of the above embodiments, the control valve unit 60 includes the first valve 71A and the second valve 71B. However, the number of valve bodies constituting the control valve unit 60 may be three or more.
For example, as shown in FIG. 13, two spacers 73 are provided between the first valve 71 </ b> A and the second valve 71 </ b> B, and the valve body 72 is disposed between the spacers 73 and 73 adjacent to each other in the central axis C direction. A third valve 71C may be provided.
As a result, the control valve unit 60 includes three valve bodies 72 including a first valve 71A, a second valve 71B, and a third valve 71C, and a third valve 71C between the first valve 71A and the third valve 71C. Between the first valve 71B and the second valve 71B, a gap channel 110 that forms the throttle portion S can be formed.

Further, as shown in FIG. 14, three spacers 73 are provided between the first valve 71A and the second valve 71B, and between the spacers 73 adjacent to each other in the central axis C direction, A third valve 71C may be provided.
Accordingly, the control valve unit 60 includes a total of four valve bodies 72, which are a first valve 71A, a second valve 71B, and two third valves 71C, between the first valve 71A and the third valve 71C. A gap channel 110 that forms the throttle portion S can be formed between the third valve 71C and the third valve 71C, and between the third valve 71C and the second valve 71B.

  Furthermore, three or more third valves 71C can be provided. In this case, n (n ≧ 2) spacers 73 are provided between the first valve 71A and the second valve 71B, and (n−1) valve bodies 72 are formed between the adjacent spacers 73. A third valve 71C is provided. According to such a configuration, a plurality of throttle portions S can be formed between the first valve 71A, the second valve 71B, and the third valve 71C stacked via the spacer 73.

According to such a configuration, the first valve 71A, the second valve 71B, and the second valve 71B are adjusted by adjusting the number of the third valves 71C stacked via the spacers 73 between the first valve 71A and the second valve 71B. The damping force generated by the oil passing between the third valves 71C can be adjusted.
As shown in FIGS. 13 and 14, even when three or more valve bodies 72 are provided, by restricting the relative rotation of the plurality of valve bodies 72 with the same configuration as the above embodiment, The flow path can be secured and the damping force can be reliably exhibited.

(Other embodiments)
The present invention is not limited to the above-described embodiments and modifications described with reference to the drawings, and various modifications can be considered within the technical scope thereof.
For example, the first valve 71A, the second valve 71B, and the third valve 71C may be formed by stacking a plurality of valve bodies 72, respectively. Also in this case, by restricting the relative rotation of the plurality of valve bodies 72 constituting the first valve 71A, the second valve 71B, and the third valve 71C, an oil flow path is secured and the damping force is ensured. Can be demonstrated.

  Further, the first valve 71A and the second valve 71B are separated by the thickness of the spacer 73 to form the gap flow path 110, but depending on the thickness of the spacer 73 to be installed, the second valve 71B When the drive valve 61 is not bent and deformed, the gap channel 110 may be configured not to generate a damping force. In this case, when the spoke 72S of the second valve 71B is bent and deformed by the drive valve 61 and the gap channel 110 is narrowed to a predetermined dimension or less, a damping force is generated in the gap channel 110.

Further, the first valve 71A may have a shape having an inner frame 75, an outer frame 74, and an opening 77 as in the case of the second valve 71B. However, the first valve 71A may have other configurations as appropriate, such as an annular plate shape. .
In addition, the outer frame 74 is not limited to an annular shape that is continuous over the entire circumference in the circumferential direction, and may be formed only at a plurality of locations at intervals in the circumferential direction.
Further, the first valve 71 </ b> A may be formed integrally with the sleeve 28. Further, the first valve 71A may be eliminated.
The second valve 71B may have a shape that does not have the center hole 76.
In addition, the first valve 71A and the second valve 71B are formed in the same shape, but are not limited to this, for example, the same shape such as the number, shape, and size of the opening 77 are different. Not necessarily.

Moreover, although the drive valve 61 was made into the shape which has the taper part 61t in the front-end | tip part, it is not restricted to this.
For example, as shown in FIG. 15, the drive valve 61 may have other shapes as appropriate as long as it has pressure receiving surfaces 120 and 121 that intersect the oil flow direction so that a pressure receiving area by oil can be secured. .

  Moreover, it is good also considering the direction of the oil flow in the compression side stroke and the extension side stroke as the opposite direction to the configuration shown in the above embodiment.

Furthermore, in the above-described embodiment, the main damper 42 and the control valve unit 60 are provided. However, the control valve unit 60 side may be a main attenuation generation unit, and the main damper 42 may be an auxiliary attenuation generation unit. In addition, the main damper 42 and the control valve unit 60 may be an equal damping force generation unit.
In addition to this, the configuration described in the above embodiment can be selected or changed to another configuration as appropriate without departing from the gist of the present invention.

DESCRIPTION OF SYMBOLS 10 ... Shock absorber 11 ... Cylinder 12 ... Piston 13 ... Piston rod 40 ... Damping force generator 42 ... Main damper (damping force generating mechanism)
50. Valve seat member (housing)
60 ... Control valve (valve mechanism)
61 ... Drive valve 62 ... Solenoid actuator (drive valve moving mechanism)
63 ... Valve seat 64 ... Valve holder (holder member)
71A ... First valve 71B ... Second valve 71C ... Third valve 72 ... Valve body 73 ... Spacer 74 ... Outer frame 75 ... Inner frame 76 ... Center hole (through hole)
77 ... Opening 80 ... Valve rotation restraint (rotation restraint)
81 ... locking claw (protrusion)
82 ... Flow passage 106 ... Central flow path (flow path)
107 ... Communication passage 110 ... Gap channel (gap)
C ... Center axis S ... Restriction part S3 ... Oil reservoir

Claims (9)

A housing having a valve seat formed radially outside the opening at one end of the fluid flow path;
A drive valve provided so as to be movable in a direction in which the valve seat comes in contact with and separates from the valve seat;
A plurality of valve bodies provided between the valve seat and the drive valve and having openings through which the fluid flows;
The drive valve is moved in a direction approaching the valve seat, and the valve body closest to the drive valve among the plurality of valve bodies is arranged such that an inner peripheral portion of the valve body has an inner peripheral portion with respect to an outer peripheral portion of the valve body. A drive valve moving mechanism that makes the gap between the inner periphery of the valve body and the valve seat variable by elastically deforming in a direction approaching the seat;
In a state where the openings of the plurality of valve bodies are in communication with each other, a rotation restraining portion that restrains relative rotation in the circumferential direction of the plurality of valve bodies;
Comprising a valve mechanism. A holder member that movably holds the drive valve on the drive valve side with respect to the valve body;
The rotation restricting portion is a protrusion that protrudes from the holder member toward the valve body and is engaged with the plurality of valve bodies.
The valve mechanism according to claim 1. The rotation restricting portion is a protrusion formed on the valve body of one of the plurality of valve bodies, protruding toward the other valve body, and formed to engage with the other valve body.
The valve mechanism according to claim 1. The protrusion is inserted into the opening of the plurality of valve bodies;
The valve mechanism according to claim 2 or 3.   The valve mechanism according to any one of claims 1 to 4, further comprising a spacer that is sandwiched between the plurality of valve bodies and that defines a gap between the plurality of valve bodies. The valve body includes an annular inner frame and an outer frame, an opening formed between the inner frame and the outer frame, and a through hole formed inside the inner frame,
The front end portion of the drive valve is reduced in diameter toward the valve seat side, and the through hole is blocked by the front end portion being seated on the inner frame. The valve mechanism according to any one of the above. The valve mechanism according to any one of claims 1 to 6,
A damping force generation device provided with a damping force generation mechanism that is provided independently of the valve mechanism and generates a damping force due to the flow of the fluid. The valve mechanism according to any one of claims 1 to 6,
A cylinder filled with fluid;
A piston slidably fitted in the cylinder;
A piston rod connected to the piston and extending to the outside of the cylinder;
An oil reservoir chamber that compensates for an amount of oil corresponding to an entry volume of the piston rod when the piston rod enters the cylinder;
A shock absorber characterized in that a fluid generated by sliding of the piston in the cylinder flows into the valve mechanism to generate a damping force, and the fluid that has passed through the valve mechanism can flow through the oil reservoir chamber. . A damping force generation mechanism that is provided independently of the valve mechanism and generates a damping force due to the flow of the fluid;
The shock absorber according to claim 8, wherein the fluid that has passed through the damping force generation mechanism can flow through the oil reservoir chamber.

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