JP2024021172A - Cylinder equipment and valve equipment - Google Patents

Abstract

The present invention provides a cylinder device and a valve device that allow damping force to be adjusted in more detail. [Solution] The inner peripheral side or the outer peripheral side is supported, the unsupported side has a gap with the case member 100 or the shaft part 28, and can be bent in one axial direction and the other axial direction. An annular disk 105, first movement restriction members 102, 103 that restrict movement of the annular disk 105 on one side in the axial direction, and second movement restriction members 107, 108 that restrict movement of the annular disk 105 on the other side in the axial direction. , a first movement distance adjusting means 104 provided between the annular disk 105 and the first movement restriction member 103 and capable of adjusting the movement distance of the annular disk 105 on one side in the axial direction; A second movement distance adjustment means 106 is provided between the member 107 and can adjust the movement distance of the annular disk 105 on the other side in the axial direction. [Selection diagram] Figure 3

Description

The present invention relates to a cylinder device and a valve device.

There is a valve that has a leaf valve that can be bent to both sides in the axial direction, and an annular opposing part that is provided with a gap between the free end of the leaf valve (for example, see Patent Document 1).

JP 2021-76139 Publication

In a cylinder device equipped with a valve as described above, it is required to adjust the damping force generated by the valve in more detail.

Therefore, an object of the present invention is to provide a cylinder device and a valve device that make it possible to adjust the damping force in more detail.

In order to achieve the above object, one aspect of the cylinder device of the present invention includes a cylinder in which a working fluid is sealed, and a piston that is slidably fitted into the cylinder and partitions the inside of the cylinder into two chambers. a piston rod having one end connected to the piston and the other end extending outside the cylinder; a first passage through which working fluid flows from one chamber in the cylinder due to movement of the piston; a second passage provided in series or parallel to the first passage; a damping force generation mechanism provided in the first passage for generating a damping force; and a cylindrical structure in which at least a portion of the second passage is formed. a case member; a shaft portion disposed within the case member; and a shaft portion penetrating the shaft portion, disposed within the case member, supported on the inner circumference side or outer circumference side, and between the case member and the case member on the non-supported side. or an annular disk having a gap between the annular disk and the shaft portion and capable of being bent in one axial direction and the other axial direction; and a first movement regulating member that restricts movement of the annular disk in the one axial direction. , a second movement restriction member for restricting movement of the annular disk on the other side in the axial direction, and a second movement restriction member provided between the annular disk and the first movement restriction member, the second movement restriction member restricting the movement distance of the annular disk on one side in the axial direction; an adjustable first movement distance adjustment means; a second movement distance adjustment means that is provided between the annular disk and the second movement restriction member and is capable of adjusting the movement distance on the other side in the axial direction of the annular disk; It was configured to have .

One aspect of the valve device of the present invention includes a cylindrical case member in which a passage is formed, a shaft portion disposed within the case member, and a shaft portion penetrating the shaft portion and disposed within the case member. , an annular disk supported on an inner circumferential side or an outer circumferential side, having a gap between the unsupported side and the case member or with the shaft portion, and capable of being bent in one axial direction and the other axial direction; , a first movement restriction member that restricts movement of the annular disk on one side in the axial direction, a second movement restriction member that restricts movement of the annular disk on the other side in the axial direction, and the annular disk and the first movement restriction member. a first movement distance adjusting means provided between the annular disk and the second movement regulating member and capable of adjusting a movement distance on one side in the axial direction of the annular disk; and a second movement distance adjusting means capable of adjusting the movement distance on the other side in the axial direction of the disk.

According to the present invention, it becomes possible to adjust the damping force in more detail.

FIG. 1 is a sectional view showing a cylinder device according to an embodiment of the present invention. FIG. 1 is a cross-sectional view of essential parts of a cylinder device according to an embodiment of the present invention. 1 is a partial cross-sectional view showing a main part of a valve device provided in a cylinder device according to an embodiment of the present invention. FIG. 2 is a partial cross-sectional view showing a state of a valve device provided in a cylinder device according to an embodiment of the present invention in a retraction stroke. FIG. 2 is a partial cross-sectional view showing a state of a valve device provided in a cylinder device according to an embodiment of the present invention during an extension stroke. FIG. 3 is a characteristic diagram showing the relationship between the opening area and the differential pressure of the annular disk of the valve device provided in the cylinder device of one embodiment of the present invention. FIG. 2 is a characteristic diagram showing the relationship between damping force and piston speed in an extremely low piston speed region of a valve device provided in a cylinder device according to an embodiment of the present invention.

An embodiment according to the present invention will be described based on the drawings. Note that, in the following description, for convenience of explanation, the upper side in FIGS. 1 to 5 will be referred to as "upper", and the lower side in FIGS. 1 to 5 will be referred to as "lower".

As shown in FIG. 1, the cylinder device 1 of this embodiment is a so-called double-tube hydraulic shock absorber, and includes a cylinder 2 in which an oil L as a working fluid is sealed. The cylinder 2 has a cylindrical inner cylinder 3 and a bottomed cylindrical outer cylinder 4 that has a larger diameter than the inner cylinder 3 and is provided concentrically so as to cover the inner cylinder 3. A reservoir chamber 6 is formed between the inner cylinder 3 and the outer cylinder 4.

The outer cylinder 4 includes a cylindrical body member 11 and a bottom member 12 that is fitted onto the lower side of the body member 11 and fixed by welding to close the lower part of the body member 11. A mounting eye 13 is fixed to the bottom member 12 by welding at an outer position opposite to the body member 11 in the axial direction.

The cylinder device 1 includes a piston 18 that is slidably provided inside the inner cylinder 3 of the cylinder 2 . The piston 18 defines two chambers within the inner cylinder 3: an upper chamber 19 that is one of the cylinder interior chambers, and a lower chamber 20 that is the other cylinder interior chamber. In other words, the piston 18 is slidably fitted into the cylinder 2 and divides the inside of the cylinder 2 into an upper chamber 19 on one side and a lower chamber 20 on the other side. An upper chamber 19 and a lower chamber 20 in the inner cylinder 3 are filled with oil L as a working fluid, and a reservoir chamber 6 between the inner cylinder 3 and the outer cylinder 4 is filled with an oil L as a working fluid. and gas G are sealed.

The cylinder device 1 includes a rod-shaped piston rod 21. The piston rod 21 has one axial end disposed inside the inner tube 3 of the cylinder 2 and connected to the piston 18, and the other end extending outside the cylinder 2. The piston rod 21 passes through the upper chamber 19 and does not penetrate the lower chamber 20. Therefore, the upper chamber 19 is a rod side chamber through which the piston rod 21 passes, and the lower chamber 20 is a bottom side chamber on the bottom side of the cylinder 2.

Piston 18 and piston rod 21 move together. In the extension stroke of the cylinder device 1 in which the piston rod 21 increases the amount of protrusion from the cylinder 2, the piston 18 moves toward the upper chamber 19 side. In the contraction stroke of the cylinder device 1 in which the piston rod 21 reduces the amount of protrusion from the cylinder 2, the piston 18 moves toward the lower chamber 20 side.

A rod guide 22 is fitted into the upper opening sides of the inner cylinder 3 and outer cylinder 4. A sealing member 23 is fitted into the outer cylinder 4 at an upper side that is outside the cylinder 2 relative to the rod guide 22 . Both the rod guide 22 and the seal member 23 have an annular shape. The piston rod 21 is slidably inserted inside each of the rod guide 22 and the seal member 23 and extends from the inside of the cylinder 2 to the outside.

The rod guide 22 guides the movement of the piston rod 21 by supporting the piston rod 21 so as to be movable in the axial direction while restricting its radial movement. The seal member 23 is in close contact with the outer cylinder 4 at its outer circumference, and comes into sliding contact at its inner circumference with the outer circumference of the piston rod 21 that moves in the axial direction. Thereby, the seal member 23 prevents the oil L in the inner cylinder 3 and the high pressure gas G and oil L in the reservoir chamber 6 in the outer cylinder 4 from leaking to the outside.

The outer circumference of the rod guide 22 has a stepped shape in which the diameter is larger at the upper part than at the lower part. The rod guide 22 fits into the inner periphery of the upper end of the inner cylinder 3 at the lower part of the small diameter, and fits into the inner periphery of the upper part of the outer cylinder 4 at the upper part of the large diameter. A base valve 25 that defines a lower chamber 20 and a reservoir chamber 6 is installed on the bottom member 12 of the outer cylinder 4. The inner peripheral portion of the lower end of the inner cylinder 3 is fitted into the base valve 25 . The upper end portion of the outer cylinder 4 is crimped radially inward to form a locking portion 26 . The locking portion 26 and the rod guide 22 sandwich the seal member 23.

The piston rod 21 has a main shaft portion 27 , a mounting shaft portion 28 having a smaller diameter than the main shaft portion 27 , and a threaded shaft portion 31 on the side of the mounting shaft portion 28 opposite to the main shaft portion 27 . The main shaft portion 27 of the piston rod 21 is slidably fitted into the rod guide 22 and the seal member 23 . The piston rod 21 has a mounting shaft portion 28 and a threaded shaft portion 31 disposed within the cylinder 2 . The piston 18 and the like are connected to the mounting shaft portion 28 . The end of the main shaft portion 27 on the mounting shaft portion 28 side forms a shaft stepped portion 29 that extends in the direction orthogonal to the axis. The mounting shaft portion 28 has a cylindrical outer peripheral surface. The threaded shaft portion 31 is provided at the tip of the piston rod 21 inside the cylinder 2, and has a male thread 32 formed on its outer periphery.

In the cylinder device 1, for example, a protruding portion of the piston rod 21 from the cylinder 2 is disposed in the upper part and supported by the vehicle body, and a mounting eye 13 on the cylinder 2 side is disposed in the lower part and connected to the wheel side. Conversely, the cylinder 2 side may be supported by the vehicle body, and the piston rod 21 may be connected to the wheel side.

As shown in FIG. 2, the piston 18 includes a metal piston body 33 connected to the piston rod 21, and an annular synthetic resin sliding member 34 integrally attached to the outer peripheral surface of the piston body 33. It is made up of. A sliding member 34 forming an outer peripheral portion of the piston 18 slides within the inner cylinder 3 .

The piston main body 33 has a perforated disk-shaped main body portion 36 at an intermediate position in the axial direction. The main body portion 36 is formed with a plurality of passage holes 37 that penetrate in the axial direction and a plurality of passage holes 39 that penetrate in the axial direction.

The plurality of passage holes 37 have a shape that extends linearly along the axial direction of the piston body 33, and are formed at equal pitches in the circumferential direction of the piston body 33. A circular annular groove 40 is formed in the piston body 33 on the side opposite to the upper chamber 19 in the axial direction, which allows the plurality of passage holes 37 to communicate with each other. On the opposite side of the annular groove 40 from the upper chamber 19, there is a first damping force generating mechanism 41 (damping force generating mechanism) that opens and closes passages in the annular groove 40 and the plurality of passage holes 37 to generate a damping force. It is provided.

By arranging the first damping force generating mechanism 41 on the side opposite to the upper chamber 19, the passages within the plurality of passage holes 37 and the annular groove 40 are prevented from moving toward the upper chamber 19 side of the piston 19, that is, elongating. This is a path on the extension side through which the oil L flows out from the upper chamber 19 on the upstream side to the lower chamber 20 on the downstream side in the stroke. The first damping force generating mechanism 41 provided for the passages in the plurality of passage holes 37 and the annular groove 40 extends from the passages in the plurality of passage holes 37 and the annular groove 40 on the extension side to the lower chamber 20. This is a damping force generation mechanism on the extension side that generates a damping force by suppressing the flow of the oil L.

The plurality of passage holes 39 have a shape that extends linearly along the axial direction of the piston body 33, and are formed at a predetermined pitch in the circumferential direction of the piston body 33. All the passage holes 39 are formed on the outer side of the piston body 33 in the radial direction than all the passage holes 37. A first damping force generation mechanism 42 (damping force generation mechanism) that opens and closes passages in the plurality of passage holes 39 to generate damping force is provided on the upper chamber 19 side of the plurality of passage holes 39 .

By disposing the first damping force generating mechanism 42 on the upper chamber 19 side, the passages in the plurality of passage holes 39 are connected to the lower chamber which is the upstream side during the movement of the piston 18 toward the lower chamber 20 side, that is, during the contraction stroke. It becomes a passage on the contraction side through which the oil L flows out from the upper chamber 19 on the downstream side. The first damping force generating mechanism 42 provided for the passages in the plurality of passage holes 39 suppresses the flow of the oil L from the passages in the plurality of passage holes 39 on the contraction side to the upper chamber 19. This is a damping force generation mechanism on the compression side that generates damping force.

The piston main body 33 has a substantially disk shape, and an insertion hole 44 is formed in the radial center of the piston body 33 so as to penetrate therethrough in the axial direction. has been done. The insertion hole 44 has a straight shape, and the mounting shaft portion 28 of the piston rod 21 is fitted into the insertion hole 44 . Thereby, the piston body 33 is positioned in the radial direction with respect to the piston rod 21.

In a portion of the piston body 33 opposite to the upper chamber 19 in the axial direction, an annular inner seat portion 46 is provided radially inwardly of the piston body 33 than the opening of the annular groove 40 on the opposite side to the upper chamber 19. is formed. In a portion of the piston body 33 opposite to the upper chamber 19 in the axial direction, a first damping force generating mechanism is provided outside the opening of the annular groove 40 in the radial direction of the piston body 33 on the opposite side to the upper chamber 19. An annular valve seat portion 47 forming a part of the valve seat 41 is formed. The inner seat portion 46 and the valve seat portion 47 protrude from the main body portion 36 toward the side opposite to the upper chamber 19 in the axial direction. An annular groove 40 is formed between the inner seat portion 46 and the valve seat portion 47. A passage groove 48 is formed in the valve seat portion 47 and passes through the valve seat portion 47 in the radial direction.

An annular inner seat portion 49 is formed at the end of the piston body 33 on the upper chamber 19 side in the axial direction, on the inner side in the radial direction of the piston body 33 than the openings on the upper chamber 19 side of the plurality of passage holes 37. There is. Further, at the end of the piston body 33 on the upper chamber 19 side in the axial direction, an annular and irregularly shaped valve seat portion 50 is provided so as to surround one or more openings on the upper chamber 19 side of the plurality of passage holes 39. It is formed. The inner seat portion 49 and the valve seat portion 50 protrude further toward the upper chamber 19 in the axial direction than the main body portion 36 . The piston body 33 is provided with a plurality of valve seat portions 50 having the same shape and spaced apart in the circumferential direction. In the valve seat portion 50, a passage groove 51 is formed in a circumferentially outer portion of the piston body 33, and passes through this portion in the radial direction. Each of the plurality of passage holes 37 is constantly in communication with the upper chamber 19 via a gap between the valve seat parts 50 adjacent to each other in the circumferential direction.

The first damping force generation mechanism 42 on the compression side includes a valve seat portion 50 of the piston body 33, and includes a plurality of disks (specifically, four disks) of the same shape in order from the piston body 33 side in the axial direction. 63, and a plurality of (specifically two) disks 64 having the same shape. On the opposite side of the disk 64 from the disk 63, one disk 65, one disk 66, and one annular member 67 are provided in order from the disk 64 side. An annular member 67 is in contact with the shaft step portion 29 of the piston rod 21 . The disks 63 to 66 and the annular member 67 are all made of metal, and each has a circular flat plate shape with a hole into which the mounting shaft portion 28 of the piston rod 21 is fitted.

The outer diameter of the disk 63 is approximately the same as the diameter of the circumscribed circle of the plurality of valve seat portions 50. The disk 64 has an outer diameter smaller than the outer diameter of the disk 63 and larger than the outer diameter of the inner seat portion 49 of the piston body 33. The disk 65 has an outer diameter smaller than the outer diameter of the disk 64 and smaller than the outer diameter of the inner seat portion 49 of the piston body 33. The disk 66 has an outer diameter larger than the outer diameter of the disk 64 and smaller than the outer diameter of the disk 63. The annular member 67 has an outer diameter smaller than the outer diameter of the disk 66 and larger than the outer diameter of the disk 64 and the outer diameter of the shaft stepped portion 29 of the piston rod 21. The annular member 67 is thicker and more rigid than the disks 63 to 66.

The plurality of disks 63 are in constant contact with the inner seat portion 49 and are seated on the valve seat portion 50 so as to be able to close the valve seat portion 50. A plurality of disks 63 and a plurality of disks 64 made of thin metal plates constitute a contraction-side main valve 71 that is flexible and can be moved into and out of the valve seat portion 50 . By separating from the valve seat portion 50, the main valve 71 allows passages in the plurality of passage holes 39 to communicate with the upper chamber 19, and suppresses the flow of the oil L between the valve seat portion 50 and the main valve 71. Generates damping force. The annular member 67 and the disk 66 prevent the main valve 71 from being deformed in the opening direction beyond a specified value.

The first damping force generation mechanism 41 on the extension side includes a valve seat portion 47 of the piston body 33, and has a plurality of (specifically two) disks 83 having the same shape. A plurality of (specifically, two) disks 84 having the same shape are provided on the opposite side of the disk 83 from the valve seat portion 47. The disks 83 and 84 are both made of metal, and each has a circular flat plate shape with a hole into which the mounting shaft portion 28 of the piston rod 21 is fitted.

The plurality of disks 83 have an outer diameter substantially equal to the outer diameter of the valve seat portion 47 of the piston body 33, and can be seated on the valve seat portion 47. The disk 84 has an outer diameter smaller than the outer diameter of the disk 83 and smaller than the outer diameter of the inner seat portion 46 of the piston body 33.

The plurality of disks 83 are in constant contact with the inner seat portion 46 and can sit on the valve seat portion 47 to close the valve seat portion 47. A plurality of disks 83 made of thin metal plates constitute an extension-side main valve 91 that is flexible and can be moved into and out of the valve seat portion 47 . When the main valve 91 is separated from the valve seat portion 47 , the passages in the plurality of passage holes 37 and the annular groove 40 can be communicated with the lower chamber 20 , and the oil fluid between the main valve 91 and the valve seat portion 47 can be communicated with each other. It suppresses the flow of L and generates damping force.

The piston body 33 includes an annular fitting cylindrical portion 95 that protrudes outward from the valve seat portion 47 in the radial direction of the piston body 33 and from the body portion 36 to the side opposite to the upper chamber 19 from the valve seat portion 47. is formed. The inner peripheral surface of the fitting cylinder portion 95 is a cylindrical surface coaxial with the insertion hole 44 .

A valve device 99 is provided on the side opposite to the upper chamber 19 in the axial direction of the plurality of disks 84 . The valve device 99 includes, in order from the disk 84 side, one case member 100, a plurality of disks 101 of the same shape (specifically, two disks), and one first stopper member 102 (first movement regulating member). , one first coupling disk 103 (first movement regulating member), one first moving distance adjusting member 104 (first moving distance adjusting means), one annular disk 105, and one first moving distance adjusting member 104 (first moving distance adjusting means). A second movement distance adjustment member 106 (second movement distance adjustment means), one second coupling disk 107 (second movement restriction member), and one second stopper member 108 (second movement restriction member). have.

As shown in FIG. 3, the case member 100, the disk 101, the first stopper member 102, the first combined disk 103, the first moving distance adjusting member 104, the annular disk 105, the second moving distance adjusting member 106, and the second connecting disk. The mounting shaft portion 28 of the piston rod 21 is fitted inside each of the second stopper member 107 and the second stopper member 108 . Case member 100, disk 101, first stopper member 102, first coupling disk 103, first moving distance adjusting member 104, annular disk 105, second moving distance adjusting member 106, second coupling disk 107, and second stopper member 108 are both made of metal and have an annular shape.

The case member 100 is a bottomed cylindrical integrally molded product. The case member 100 has a bottom portion 111, an outer tube portion 112, an inner tube portion 113, and a seat portion 114. The bottom part 111, the outer cylindrical part 112, the inner cylindrical part 113, and the seat part 114 are all annular, and their central axes are aligned with each other. This central axis becomes the central axis of the case member 100. A mounting shaft portion 28 of the piston rod 21 is arranged within the case member 100. This mounting shaft portion 28 also constitutes a valve device 99.

The bottom portion 111 has a holed disk shape, and the mounting shaft portion 28 of the piston rod 21 is fitted into the inner peripheral portion of the bottom portion 111 . A passage hole 121 is formed in the bottom portion 111 and passes through the bottom portion 111 in the axial direction of the bottom portion 111 . A plurality of passage holes 121 having the same shape are provided in the bottom portion 111 at equal intervals in the circumferential direction of the bottom portion 111 .

The outer cylindrical portion 112 has a substantially cylindrical shape and extends from the outer peripheral edge of the bottom portion 111 to one side in the axial direction of the bottom portion 111 . The outer cylinder part 112 has an enlarged diameter part 125 and a cylindrical part 126.

The enlarged diameter portion 125 is located closest to the bottom portion 111 in the axial direction of the outer cylinder portion 112, and protrudes from the outer peripheral edge of the bottom portion 111 toward one side of the bottom portion 111 in the axial direction while increasing its diameter.

The cylindrical portion 126 has a cylindrical shape and extends from the end of the enlarged diameter portion 125 on the opposite side to the bottom portion 111 in the axial direction so as to move away from the bottom portion 111 in the axial direction of the enlarged diameter portion 125 .

The inner cylinder part 113 has a substantially cylindrical shape, and the mounting shaft part 28 of the piston rod 21 is fitted into the inner peripheral part thereof. The inner cylinder part 113 extends from the inner circumferential edge of the bottom part 111 to the same side as the outer cylinder part 112 in the axial direction of the bottom part 111 . The amount of extension of the inner cylindrical portion 113 from the bottom portion 111 is smaller than the amount of extension of the outer cylindrical portion 112 from the bottom portion 111 . The passage hole of the bottom part 111 is provided between the outer cylinder part 112 and the inner cylinder part 113 in the radial direction of the bottom part 111.

The seat portion 114 protrudes inward from the inner peripheral surface 130 of the cylindrical portion 126 of the outer cylinder portion 112 in the radial direction of the cylindrical portion 126 . The seat portion 114 has a mirror-symmetrical shape in the axial direction.
The seat portion 114 has a first seat surface 131 , a first inclined surface 132 , an opposing surface 133 , a second inclined surface 134 , and a second seat surface 135 .

The first seat surface 131 is located closest to the bottom 111 in the axial direction of the seat portion 114 among the first seat surface 131, the first inclined surface 132, the opposing surface 133, the second inclined surface 134, and the second seat surface 135. be. The first seat surface 131 extends inward in the radial direction of the cylindrical portion 126 from the inner circumferential surface 130 of the cylindrical portion 126 . The first seat surface 131 has a circular shape that spreads from the entire circumference of the inner circumferential surface 130 of the cylindrical portion 126, and has a planar shape that spreads perpendicularly to the central axis of the case member 100.

The first inclined surface 132 extends from the radially inner inner circumferential edge of the first seat surface 131 toward the side opposite to the bottom 111 in the axial direction of the seat portion 114 . The first inclined surface 132 is a tapered surface whose diameter becomes smaller as the distance from the bottom portion 111 increases in the axial direction of the seat portion 114.

The opposing surface 133 extends in a direction away from the bottom 111 from an edge of the first inclined surface 132 on the opposite side to the bottom 111 in the axial direction of the seat portion 114 . The opposing surface 133 is a cylindrical surface centered on the central axis of the case member 100 . The diameter of the opposing surface 133 is smaller than the diameter of the inner circumferential surface 130 of the cylindrical portion 126.

The second inclined surface 134 extends in a direction away from the bottom 111 from an end edge of the opposing surface 133 on the opposite side to the bottom 111 in the axial direction. The second inclined surface 134 is a tapered surface whose diameter becomes smaller as the distance from the bottom portion 111 increases in the axial direction of the seat portion 114. The second inclined surface 134 has mirror symmetry with the first inclined surface 132.

Among the first seat surface 131, the first inclined surface 132, the opposing surface 133, the second inclined surface 134, and the second seat surface 135, the second seat surface 135 is located at the bottom 111 in the axial direction of the seat portion 114. It's on the opposite side. The second seat surface 135 spreads outward in the radial direction of the seat portion 114 from the end edge of the second inclined surface 134 opposite to the bottom portion 111 in the axial direction, and extends to the inner circumferential surface 130 of the cylindrical portion 126. It is connected. The second seat surface 135 has a circular shape that spreads from the entire circumference of the inner circumferential surface 130 of the cylindrical portion 126, and has a planar shape that spreads perpendicularly to the central axis of the case member 100. The second sheet surface 135 is mirror-symmetrical to the first sheet surface 131.

The case member 100 fits into the fitting cylinder part 95 of the piston 18 at the bottom part 111. The case member 100 abuts the disk 84 at the end surface of the bottom portion 111 on the side opposite to the inner cylinder portion 113 in the axial direction. The passage hole 121 of the bottom portion 111 is provided at a position outside the disk 84 and inside the fitting cylinder portion 95 in the radial direction of the bottom portion 111 .

The disk 101, the first stopper member 102, the first coupling disk 103, the first moving distance adjusting member 104, the annular disk 105, the second moving distance adjusting member 106, the second coupling disk 107, and the second stopper member 108 are case members. 100 is disposed within an outer cylindrical portion 112.

The disk 101 has a circular flat plate shape with holes. The outer diameter of the disk 101 is equal to the outer diameter of the end surface of the inner cylinder portion 113 on the side opposite to the bottom portion 111 in the axial direction. The disk 101 abuts against this end surface of the inner cylindrical portion 113.

The first stopper member 102 has a circular plate shape with a hole, and the thickness becomes thinner toward the outer side in the radial direction. The first stopper member 102 comes into contact with the opposite side of the disk 101 from the inner cylindrical portion 113 in the axial direction at one end surface in the axial direction.

The first stopper member 102 has a regulating surface 141 on the side opposite to the bottom portion 111 in the axial direction. The regulating surface 141 extends from the intermediate position in the radial direction of the first stopper member 102 to the outer end position. The regulating surface 141 is a tapered surface that slopes so that the further outward in the radial direction of the first stopper member 102, the closer to the bottom 111 in the axial direction of the first stopper member 102.

A passage groove 142 is formed in the first stopper member 102 and is recessed from the regulating surface 141 in the axial direction of the first stopper member 102 . The passage groove 142 extends along the radial direction of the regulating surface 141 from an intermediate position in the radial direction of the regulating surface 141 and exits to the outer end position of the regulating surface 141 in the radial direction. A plurality of passage grooves 142 having the same shape are provided in the first stopper member 102 at equal intervals in the circumferential direction.

The first coupling disk 103 is a circular plate-shaped disk with a hole. The first coupling disk 103 has a main body portion 151 and a protrusion portion 152 .
The main body portion 151 has a circular flat plate shape with a hole, and the mounting shaft portion 28 of the piston rod 21 is fitted into the inner peripheral portion thereof. A notch 155 and a passage hole 156 are formed in the main body portion 151 .

The notch 155 is formed on the outer circumference of the main body 151 and extends radially outward of the main body 151 . The notch 155 penetrates the main body 151 in the axial direction of the main body 151. The main body portion 151 is provided with a plurality of cutouts 155 of the same shape at equal intervals in the circumferential direction.

The passage hole 156 is formed inside the notch 155 in the radial direction of the main body portion 151. The passage hole 156 passes through the main body 151 in the axial direction of the main body 151 . The passage hole 156 is an elongated hole extending in the circumferential direction of the main body portion 151. The main body portion 151 is provided with a plurality of passage holes 156 of the same shape at equal intervals in the circumferential direction. The plurality of passage holes 156 are arranged at positions equidistant from the center of the main body portion 151.

The protruding part 152 has a circular flat plate shape with a hole, is arranged coaxially with the main body part 151, and is bonded and fixed by welding.
The protrusion 152 protrudes from the main body 151 to one side in the axial direction of the main body 151 . The protruding portion 152 has an annular shape that is formed over the entire circumference of the main body portion 151 in the circumferential direction. The protruding portion 152 is arranged between the notch 155 and the passage hole 156 in the radial direction of the main body portion 151 .

In the first coupling disk 103, a radially inner portion of the main body portion 151 abuts an end surface of the first stopper member 102 on the side opposite to the disk 101 in the axial direction. At this time, the first coupling disk 103 is oriented such that the protruding portion 152 protrudes from the main body portion 151 in the axial direction of the first coupling disk 103 on the opposite side to the first stopper member 102 .

In the first coupling disk 103, the outer diameter of the main body portion 151 is larger than the inner diameter of the first seat surface 131 of the seat portion 114 of the case member 100, and is larger than the inner diameter of the inner peripheral surface 130 of the cylindrical portion 126. It is also small in diameter. In the first coupling disk 103 , the outer diameter of the protruding portion 152 is smaller than the inner diameter of the opposing surface 133 of the seat portion 114 . In the first coupling disk 103, the notch 155 and the passage hole 156 are both aligned with the passage groove 142 of the first stopper member 102 in the radial direction of the first coupling disk 103 and the first stopper member 102. .

As shown in FIG. 4, when the first coupling disk 103 deforms toward the first stopper member 102, the main body portion 151 comes into contact with the restriction surface 141 of the first stopper member 102, and the deformation is restricted. Even in this state, the passage within the passage groove 142 of the first stopper member 102 communicates with the passage within the passage hole 156 of the first coupling disk 103.

The first moving distance adjusting member 104 has a circular flat plate shape with a hole, and the mounting shaft portion 28 of the piston rod 21 is fitted into the inner peripheral portion thereof. The outer end position of the first moving distance adjusting member 104 is inside the passage hole 156 in the radial direction of the first coupling disk 103. The first movement distance adjusting member 104 abuts on the inner side of the main body portion 151 of the first coupling disk 103 in the radial direction, on the side opposite to the first stopper member 102 in the axial direction of the first coupling disk 103 .

The annular disk 105 has a circular flat plate shape with a hole, and the mounting shaft portion 28 of the piston rod 21 is fitted into the inner peripheral portion thereof. The annular disk 105 has an outer diameter larger than the outer diameter of the protruding portion 152 of the first coupling disk 103 and slightly smaller than the inner diameter of the opposing surface 133 of the seat portion 114. The inner portion of the annular disk 105 in the radial direction abuts the first moving distance adjusting member 104 on the side opposite to the first coupling disk 103 in the axial direction. The first stopper member 102 and the first coupling disk 103 restrict movement or deformation of the annular disk 105 toward the first stopper member 102 .

The second moving distance adjusting member 106 has a circular flat plate shape with a hole, and the mounting shaft portion 28 of the piston rod 21 is fitted into the inner peripheral portion thereof. The second moving distance adjusting member 106 has an outer diameter equivalent to the outer diameter of the first moving distance adjusting member 104. The second moving distance adjusting member 106 abuts on the inner side of the annular disk 105 in the radial direction, on the side opposite to the first moving distance adjusting member 104 in the axial direction of the annular disk 105 .

The second coupling disk 107 is a common part having the same shape as the first coupling disk 103. The second coupling disk 107 has a body portion 161 similar to the body portion 151 , a protrusion 162 similar to the protrusion 152 , a notch 165 similar to the notch 155 , and a passage hole 166 similar to the passage hole 156 . are doing.

In the second coupling disk 107, the radially inner portion of the main body portion 161 abuts the second moving distance adjusting member 106 on the opposite side of the annular disk 105 in the axial direction. At this time, the second joint disc 107 is oriented such that the protrusion 162 projects from the main body 161 toward the annular disc 105 in the axial direction of the second joint disc 107 .

In the second coupling disk 107, the outer diameter of the main body portion 161 is larger than the inner diameter of the second seat surface 135 of the seat portion 114 of the case member 100, and is larger than the inner diameter of the inner circumferential surface 130 of the cylindrical portion 126. It is also small in diameter. In the second coupling disk 107 , the outer diameter of the protruding portion 162 is smaller than the inner diameter of the opposing surface 133 of the seat portion 114 .

The second stopper member 108 is a common part having the same shape as the first stopper member 102. The second stopper member 108 comes into contact with the radially inner portion of the main body portion 161 of the second coupling disk 107 on the side opposite to the second movement distance adjusting member 106 in the axial direction, at one end surface in the axial direction. The second stopper member 108 has a regulating surface 171 similar to the regulating surface 141 and a passage groove 172 similar to the passage groove 142. The second stopper member 108 is arranged in mirror symmetry with the first stopper member 102. Therefore, the regulating surface 171 of the second stopper member 108 faces the second coupling disk 107 .

In the second coupling disk 107, the notch 165 and the passage hole 166 are both aligned with the passage groove 172 of the second stopper member 108 in the radial direction of the second coupling disk 107 and the second stopper member 108.

As shown in FIG. 5, when the second coupling disk 107 deforms toward the second stopper member 108, the main body portion 161 comes into contact with the restriction surface 171 of the second stopper member 108, thereby restricting the deformation. Even in this state, the passage within the passage groove 172 of the second stopper member 108 communicates with the passage within the passage hole 166 of the second coupling disk 107. The second stopper member 108 and the second coupling disk 107 restrict movement or deformation of the annular disk 105 toward the second stopper member 108 .

As shown in FIG. 2, the threaded shaft portion 31 of the piston rod 21 projects on the opposite side of the second coupling disk 107 in the axial direction of the second stopper member 108. As shown in FIG. A nut 191 is screwed onto the screw shaft portion 31 . Thereby, the parts from the annular member 67 to the second stopper member 108 are clamped in the axial direction at least at the inner peripheral portion.

The annular disk 105 attached to the piston rod 21 has a flat plate shape in an initial state where pressures on both sides in the axial direction are equal. In this state, the annular disk 105 is aligned in the axial direction with the facing surface 133 of the seat portion 114 of the case member 100, as shown in FIG. At this time, the annular disk 105 has a slight gap in the radial direction between it and the opposing surface 133. The annular disk 105 expands the passage between it and the seat part 114 by deforming and moving to one side in the axial direction, and expands the passage between it and the seat part 114 by deforming and moving to the other side in the axial direction. It is an expanding swing valve.

When the pressure on the bottom 111 side in the axial direction is greater than or equal to the pressure on the opposite side to the bottom 111, the first coupling disk 103 attached to the piston rod 21 moves outward from the protrusion 152 in the radial direction of the main body 151. The outer circumferential side of the seat member 12 contacts the first seat surface 131 of the seat portion 114 .

Here, the thickness of the disk 101 is adjusted, that is, a disk 101 with an appropriate thickness is selected from a plurality of types of disks 101 having different thicknesses and attached to the piston rod 21. Thereby, it is possible to adjust the initial deflection amount of the main body portion 151 in contact with the first seat surface 131 in an initial state where the pressure on both sides of the first coupling disk 103 in the axial direction is equal. That is, the thicker the disk 101 is, the closer the inner peripheral sides of the main body portion 151 of the first stopper member 102 and the first combined disk 103 are to the facing surface 133 of the seat portion 114 in the axial direction, As a result, the initial deflection amount of the main body portion 151 that contacts the first seat surface 131 on the outer circumferential side increases, and the main body portion 151 approaches the regulating surface 141 of the first stopper member 102 . The larger the initial deflection amount of the first coupling disk 103, the larger the set load.

In the initial state, the first coupling disk 103 contacts the first seat surface 131 of the seat section 114 in the main body section 151 . At this time, the notch 155 of the main body portion 151 extends further inward in the radial direction than the first seat surface 131 .

The thickness of the first moving distance adjusting member 104 is adjusted according to the thickness of the disk 101 so that the axial position of the annular disk 105 coincides with the facing surface 133 of the seat portion 114 as described above. . That is, one with an appropriate thickness is selected from a plurality of types of first movement distance adjusting members 104 having different thicknesses, and is attached to the piston rod 21, and the axial position of the annular disk 105 is adjusted as described above. It is made to coincide with the opposing surface 133 of the seat portion 114.

In other words, when adjusting the thickness of the disk 101 as described above, the thickness of the first movement distance adjusting member 104 is also adjusted so that the axial position of the annular disk 105 coincides with the facing surface 133 of the seat portion 114. and attach it to the piston rod 21. Thereby, the amount of initial deflection of the main body portion 151 of the first coupling disk 103 that comes into contact with the first sheet surface 131 can be adjusted. That is, the thicker the disk 101 is, the thinner the first moving distance adjusting member 104 is, and as a result, the main body portion 151 of the first stopper member 102 and the first coupling disk 103 is made thinner. Since the inner circumferential side approaches the seat portion 114 in the axial direction, the initial deflection amount of the main body portion 151 that contacts the first seat surface 131 on the outer circumferential side increases.

The disk 101 and the first movement distance adjusting member 104 adjust the initial deflection amount of the first coupling disk 103 to adjust the relationship between the protrusion 152 of the first coupling disk 103 and the annular disk 105 in an initial state with no differential pressure. Adjust clearance. In addition, the disk 101 and the first movement distance adjusting member 104 adjust the initial deflection amount of the first coupling disk 103, so that the first coupling disk 103 changes from the initial state with no differential pressure to the position of the first stopper member 102. The amount of deformation, that is, the amount of movement, is adjusted until it comes into contact with the regulating surface 141 and deformation, that is, movement is regulated. In other words, the disk 101 and the first movement distance adjusting member 104 adjust the amount of deformation, that is, the amount of movement that can be made until the first combined disk 103 comes into contact with the regulating surface 141.

Specifically, the larger the initial deflection amount of the first combined disk 103, the more the disk 101 and the first moving distance adjusting member 104 will be able to change the relationship between the protrusion 152 of the first combined disk 103 and the annular disk 105 in the initial state. At the same time, the amount of deformation that the first coupling disk 103 can deform until it comes into contact with the regulating surface 141 is reduced. However, in the initial state, the thickness of the disk 101 and the first moving distance adjusting member 104 is set so that the protrusion 152 of the first combined disk 103 does not come into contact with the annular disk 105 and a clearance is secured. .

If the pressure on the side opposite to the bottom 111 in the axial direction is greater than or equal to the pressure on the bottom 111 side, the second coupling disk 107 attached to the piston rod 21 moves outward from the protrusion 162 in the radial direction of the main body 161. The outer circumferential side of the seat portion 114 contacts the second seat surface 135 of the seat portion 114 .

Here, the thickness of the second movement distance adjustment member 106 is adjusted, that is, one with an appropriate thickness is selected from a plurality of types of second movement distance adjustment members 106 having different thicknesses, and is attached to the piston rod 21. . Thereby, the amount of initial deflection of the second coupling disk 107 when it comes into contact with the second sheet surface 135 can be adjusted. That is, the thinner the second moving distance adjusting member 106 is, the closer the inner peripheral side of the main body portion 161 of the second stopper member 108 and the second coupling disk 107 is to the facing surface 133 of the seat portion 114 in the axial direction. As a result, the amount of initial deflection of the main body portion 161 that contacts the second seat surface 135 on the outer circumferential side increases. The larger the initial deflection amount of the second coupling disk 107, the larger the set load.

In the initial state, the second coupling disk 107 contacts the second seat surface 135 of the seat portion 114 in the main body portion 161 . At this time, the notch 165 of the main body portion 161 extends further inward in the radial direction than the second seat surface 135.

The second movement distance adjustment member 106 adjusts the clearance between the protrusion 162 of the second joint disc 107 and the annular disc 105 in an initial state with no differential pressure by adjusting the initial deflection amount of the second joint disc 107. do. In addition, the second movement distance adjusting member 106 adjusts the initial deflection amount of the second coupling disc 107 so that the second coupling disc 107 changes from the initial state with no differential pressure to the regulating surface 171 of the second stopper member 108. The amount of deformation, that is, the amount of movement, is adjusted until it comes into contact with and restricts deformation, that is, movement. In other words, the second movement distance adjustment member 106 adjusts the amount of deformation, that is, the amount of movement that can be made until the second coupling disk 107 comes into contact with the regulating surface 171 .

Specifically, the second movement distance adjusting member 106 increases the clearance between the protrusion 162 of the second joint disc 107 and the annular disc 105 in the initial state as the initial deflection amount of the second joint disc 107 increases. At the same time, the amount of deformation, that is, the amount of movement that the main body portion 161 of the second coupling disk 107 can deform until it comes into contact with the regulating surface 171 is made smaller. However, the thickness of the second moving distance adjusting member 106 is set in the initial state so that the protruding portion 162 of the second coupling disk 107 does not come into contact with the annular disk 105 and a clearance is secured.

In this embodiment, the second moving distance adjusting member 106 is thinner than the first moving distance adjusting member 104. As a result, the second combined disk 107 has a larger initial deflection amount than the first combined disk 103.

As shown in FIG. 4, when the annular disk 105 deforms and moves toward the first coupling disk 103, it comes into contact with the protrusion 152 of the first coupling disk 103. In this state, when the annular disk 105 further deforms, the first coupling disk 103 is deformed and moved toward the first stopper member 102 side. When the annular disk 105 is deformed until the first coupling disk 103 comes into contact with the restriction surface 141 of the first stopper member 102, further deformation or movement toward the first stopper member 102 is restricted.

The amount of deformation, that is, the amount of movement (movement distance) of the annular disk 105 is determined depending on the amount of deformation of the first coupling disk 103 from the initial state until it comes into contact with the regulating surface 141 of the first stopper member 102 . That is, the greater the amount of deformation of the annular disk 105 from the initial state of the first coupling disk 103 until it abuts the regulating surface 141 of the first stopper member 102, the greater the amount of deformation, that is, the amount of movement.

Therefore, the first movement distance adjustment member 104 that adjusts the amount of deformation of the first coupling disk 103 from its initial state to when it comes into contact with the regulating surface 141 of the first stopper member 102 is adjusted in the axial direction from the initial state of the annular disk 105. The amount of deformation, that is, the distance of movement toward one side, the first stopper member 102, can be adjusted.

When the annular disk 105 deforms and moves toward the second coupling disk 107 , it comes into contact with the protrusion 162 of the second coupling disk 107 . When the annular disk 105 further deforms in this state, the second coupling disk 107 is deformed and moved toward the second stopper member 108 . When the annular disk 105 deforms the second coupling disk 107 until it comes into contact with the restriction surface 171 of the second stopper member 108, further deformation or movement toward the second stopper member 108 is restricted.

The amount of deformation, that is, the amount of movement (movement distance) of the annular disk 105 is determined depending on the amount of deformation of the second coupling disk 107 from the initial state until it comes into contact with the regulating surface 171 of the second stopper member 108 . That is, the greater the amount of deformation of the annular disk 105 from the initial state of the second coupling disk 107 until it abuts the regulating surface 171 of the second stopper member 108, the greater the amount of deformation, that is, the amount of movement.

Therefore, the second movement distance adjusting member 106 that adjusts the amount of deformation of the second coupling disk 107 from its initial state to when it comes into contact with the regulating surface 171 of the second stopper member 108 is adjusted in the axial direction from the initial state of the annular disk 105. The amount of deformation, that is, the distance of movement toward the second stopper member 108 side, which is the other side, can be adjusted.

The first coupling disk 103, the first moving distance adjusting member 104, the annular disk 105, the second moving distance adjusting member 106, and the second coupling disk 107 constitute the sub-valve 201. The sub-valve 201 increases or decreases the passage area between the sub-valve 201 and the seat portion 114 of the case member 100 depending on the differential pressure in its axial direction. The sub-valve 201 and the seat portion 114 constitute a second damping force generation mechanism 202 that is common to the extension stroke and the contraction stroke.

As described above, as shown in FIG. 3, the annular disk 105 of the valve device 99 is disposed within the case member 100 so as to pass through the mounting shaft portion 28 of the piston rod 21. The annular disk 105 is supported by the mounting shaft portion 28 on its inner circumferential side, and has a gap between it and the seat portion 114 of the case member 100 on its outer circumferential side, which is the unsupported side. The annular disk 105 is flexible in one axial direction and in the other axial direction.

The first stopper member 102 of the valve device 99 restricts the movement of the annular disk 105 in one axial direction by the first coupling disk 103 .
The second stopper member 108 of the valve device 99 restricts the movement of the annular disk 105 on the other side in the axial direction by the second coupling disk 107 .

The first travel distance adjusting member 104 of the valve device 99 is provided between the annular disk 105 and the first coupling disk 103. The first moving distance adjusting member 104 can adjust the moving distance of the annular disk 105 on one side in the axial direction.
The second travel distance adjusting means 106 of the valve device 99 is provided between the annular disk 105 and the second coupling disk 107. The second moving distance adjusting means 106 can adjust the moving distance of the annular disk 105 on the other side in the axial direction.

A portion surrounded by the piston 18, the bottom of the case member 100, and the disks 83 and 84 forms a valve chamber 205.
A portion surrounded by the sub-valve 201, the case member 100, the disk 101, and the first stopper member 102 is a case chamber 206. A portion surrounded by the sub-valve 201, the case member 100, and the second stopper member 108 forms a communication chamber 207 that is constantly in communication with the lower chamber 20.

Inside the sub-valve 201, a portion surrounded by the first coupling disk 103, the first moving distance adjusting member 104, the annular disk 105, and the seat portion 114 forms a first valve inner chamber 208. The first valve interior chamber 208 communicates with the case chamber 206 via a passage in the notch 155 and in the passage hole 156 of the first coupling disc 103 .

Inside the sub-valve 201, a portion surrounded by the second coupling disk 107, the second moving distance adjusting member 106, the annular disk 105, and the seat portion 114 forms a second valve inner chamber 209. The second valve internal chamber 209 communicates with the communication chamber 207 via a passage in the notch 165 and the passage hole 166 of the second coupling disk 107 .

When the piston 18 shown in FIG. 2 moves to the extension side, the oil L in one upper chamber 19 in the cylinder 2 flows from the upper chamber 19 to the passage in the passage hole 37 of the piston 18 and the annular groove 40, and the piston into the valve chamber 205 through an expansion introduction side passage 211 (first passage) consisting of a passage in the passage groove 48 of the valve seat part 47 or a passage between the valve seat part 47 and the main valve 91 to be opened. flows. In other words, as the piston 18 moves, the oil L flows out from one upper chamber 19 in the cylinder 2 to the extension introduction side passage 211 .

The oil L from the upper chamber 19 that has flowed into the valve chamber 205 flows through the valve chamber 205, the passage in the passage hole 121 of the case member 100 of the valve device 99, the case chamber 206, the sub-valve 201, and the seat portion 114. It flows out into the lower chamber 20 through an elongated discharge side passage 212 (second passage) consisting of a passage between and a communication chamber 207.

The extension introduction side passage 211 and the extension discharge side passage 212 are provided in series.
The first damping force generation mechanism 41 is provided in the extension introduction side passage 211, and is used when flowing the oil L from the upper chamber 19 into the lower chamber 20 via the extension introduction side passage 211 and the extension discharge side passage 212. , generates a damping force.

The sub-valve 201 is provided in the expansion discharge side passage 212, and generates a damping force when the oil L from the upper chamber 19 flows into the lower chamber 20 via the expansion introduction side passage 211 and the expansion discharge side passage 212. let

A portion of the elongated discharge side passage 212 is formed inside the cylindrical case member 100. The entire extension and discharge side passage 212 may be formed inside the case member 100.

When the piston 18 moves to the contraction side, the oil L in the lower chamber 20 in the cylinder 2 flows from the lower chamber 20 to the communication chamber 207 of the valve device 99 and the passage between the sub-valve 201 and the seat portion 114. It flows into the case chamber 206 via the contraction introduction side passage 221 (second passage) consisting of.

The oil L flowing into the case chamber 206 then flows through the case chamber 206, the passage in the passage hole 121 of the case member 100, the valve chamber 205, the passage in the passage hole 39 of the piston 18, and the valve of the piston 18. It flows into the upper chamber 19 through a contraction discharge side passage 222 (first passage) consisting of a passage in the passage groove 51 of the seat part 50 or a passage between the valve seat part 50 and the main valve 71 to be opened. In other words, as the piston 18 moves, the oil L flows out from the other lower chamber 20 in the cylinder 2 through the contraction introduction passage 221 and from the contraction discharge passage 222 into the upper chamber 19 .

The contraction introduction side passage 221 and the contraction discharge side passage 222 are provided in series.
The sub-valve 201 is provided in the contraction introduction side passage 221, and generates a damping force when the oil L from the lower chamber 20 flows into the upper chamber 19 via the contraction introduction side passage 221 and the contraction discharge side passage 222. let
The first damping force generation mechanism 42 is provided in the contraction discharge side passage 222, and is used when flowing the oil L from the lower chamber 20 into the upper chamber 19 via the contraction introduction side passage 221 and the contraction discharge side passage 222. , generates a damping force.
The entire contraction introduction side passage 221 is formed inside the cylindrical case member 100. A part of the contraction introduction side passage 221 may be formed inside the case member 100.

As shown in FIG. 1, the above-described base valve 25 is provided between the bottom member 12 of the outer cylinder 4 and the inner cylinder 3. This base valve 25 includes a base valve member 251 that partitions the lower chamber 20 and the reservoir chamber 6, a disc valve 252 provided on the lower side of the base valve member 251, that is, on the reservoir chamber 6 side, and the upper side of the base valve member 251, that is, on the reservoir chamber 6 side. It has a disk valve 253 provided on the lower chamber 20 side, and a mounting pin 254 for attaching the disk valve 252 and the disk valve 253 to the base valve member 251.

The base valve member 251 has an annular shape, and a mounting pin 254 is inserted through the center in the radial direction. The base valve member 251 has a plurality of passage holes 255 through which the oil L can flow between the lower chamber 20 and the reservoir chamber 6, and a plurality of passage holes 255 on the outside of the base valve member 251 in the radial direction from these passage holes 255. A plurality of passage holes 256 are formed between the lower chamber 20 and the reservoir chamber 6 through which the oil L can flow. The disc valve 252 on the side of the reservoir chamber 6 allows the oil L to flow from the lower chamber 20 to the reservoir chamber 6 through the passage hole 255, while allowing the oil L to flow from the reservoir chamber 6 to the lower chamber 20 through the passage hole 255. Suppress the flow of liquid L. The disc valve 253 allows the oil L to flow from the reservoir chamber 6 to the lower chamber 20 through the passage hole 256, while preventing the oil L from flowing from the lower chamber 20 to the reservoir chamber 6 through the passage hole 256. suppress.

The disc valve 252 and the base valve member 251 operate a compression-side damping valve mechanism 257 that opens during the compression stroke of the cylinder device 1 to flow the oil L from the lower chamber 20 to the reservoir chamber 6 and generates a damping force. It consists of The disc valve 253 and the base valve member 251 constitute a suction valve mechanism 258 that opens during the extension stroke of the cylinder device 1 and allows the oil L to flow from the reservoir chamber 6 into the lower chamber 20. The suction valve mechanism 258 supplies the oil L from the reservoir chamber 6 to the lower chamber 20 without substantially generating damping force, mainly to compensate for the lack of liquid caused by the extension of the piston rod 21 from the cylinder 2. It performs the function of flowing.

Of the first damping force generation mechanism 41 and the second damping force generation mechanism 202 shown in FIG. It is more rigid and has a higher opening pressure. In an extremely low speed region where the piston speed is lower than a predetermined value, the first damping force generating mechanism 41 is closed and the second damping force generating mechanism 202 is opened. Further, in the extension stroke, in a normal speed range where the piston speed is equal to or higher than this predetermined value, both the first damping force generation mechanism 41 and the second damping force generation mechanism 202 open. In other words, the first damping force generation mechanism 41 is provided in the extension passage 211, and is closed in a region where the piston speed is low, and opened in a speed region where the piston speed is higher than the low speed. Further, the second damping force generation mechanism 202 is provided in an extension discharge side passage 212 that is in series with the extension introduction passage 211, and opens from a region where the piston speed is low. The sub-valve 201 is an extremely low-speed valve that opens in a region where the piston speed is extremely low to generate damping force.

In the extension stroke, the piston 18 moves toward the upper chamber 19, thereby increasing the pressure in the upper chamber 19 and decreasing the pressure in the lower chamber 20. During the extension stroke when the piston speed is less than the first predetermined value, the oil L in the upper chamber 19 flows into the lower chamber 20 via the extension introduction side passage 211 and the extension discharge side passage 212. The first damping force generating mechanism 41 of the introduction side passage 211 does not open, and the second damping force generating mechanism 202 also does not open. Therefore, the oil L in the upper chamber 19 flows through the passages in the passage hole 37 and the annular groove 40, the passage in the passage groove 48 of the valve seat portion 47, the valve chamber 205, the passage in the passage hole 121, and the case chamber 206. , flows into the lower chamber 20 through the gap between the annular disk 105 and the facing surface 133 of the seat portion 114, which overlap each other in the axial direction, and the communication chamber 207, as shown in FIG. This causes the damping force to rise rapidly.

During the extension stroke when the piston speed is greater than or equal to the first predetermined value and less than the second predetermined value, the first damping force generating mechanism 41 of the extension introduction side passage 211 does not open, and the oil L in the upper chamber 19 flows through the valve. As shown in FIG. It flows into the lower chamber 20 while opening.

At this time, the oil L from the case chamber 206 is introduced into the first valve inner chamber 208 from the passage in the notch 155 of the first coupling disk 103 and the passage hole 156 in the sub-valve 201 . Then, the pressure inside the first valve inner chamber 208 increases, causing the annular disk 105 to bend toward the communication chamber 207 and away from the seat portion 114, and also to push the annular disk 105 into contact with the protrusion 162 of the second coupling disk 107. The second coupling disk 107 is bent toward the communication chamber 207 and separated from the seat portion 114 . Thereby, in the extension stroke, even in an extremely low speed region where the piston speed is greater than or equal to the first predetermined value and less than the second predetermined value, a damping force having a valve characteristic (a characteristic in which the damping force is substantially proportional to the piston speed) can be obtained.

At this time, as shown in FIG. 5, the sub-valve 201 is deformed or moved by the amount of deformation or movement of the annular disk 105 until the second coupling disk 107 comes into contact with the second stopper member 108 and the deformation or movement is regulated. 114, that is, the maximum opening area at maximum valve opening, that is, the maximum opening area between the annular disk 105 and the seat portion 114. If the second movement distance adjusting member 106 is thin and the amount of deformation, that is, the amount of movement of the annular disk 105 until the second coupling disk 107 comes into contact with the second stopper member 108 is small, the annular disk 105 and the seat at the maximum valve opening are The maximum opening area between the portions 114 becomes smaller, and the generated damping force becomes higher. On the other hand, if the second movement distance adjusting member 106 is thick and the amount of deformation, that is, the amount of movement of the annular disk 105 until the second coupling disk 107 comes into contact with the second stopper member 108 is large, the annular disk 105 at the maximum valve opening is The maximum opening area between the seat portions 114 becomes larger, and the generated damping force becomes lower.

Further, in the extension stroke, in the normal speed region where the piston speed is equal to or higher than the second predetermined value, the first damping force generating mechanism 41 shown in FIG. 3 opens while the second damping force generating mechanism 202 remains open. . That is, as described above, the annular disk 105 and the second coupling disk 107 of the sub-valve 201 of the second damping force generation mechanism 202 are separated from the seat part 114, and the upper chamber 19 is moved from the lower chamber 20 in the expansion discharge side passage 212 on the expansion side. At this time, the flow of the oil L is restricted in the passage in the passage groove 48, which serves as an orifice, provided upstream of the sub-valve 201 in the extension introduction side passage 211. , the pressure applied to the main valve 91 increases, the differential pressure increases, and the main valve 91 separates from the valve seat portion 47, causing the main valve 91 to move downward from the upper chamber 19 in the extension-inlet passage 211 and the extension-discharge passage 212 on the extension side. The oil liquid L is flowed into the chamber 20. Thereby, in the extension stroke, even in the normal speed range where the piston speed is equal to or higher than the second predetermined value, a damping force having a valve characteristic (the damping force is approximately proportional to the piston speed) can be obtained.

The rate of increase in the damping force on the extension side with respect to an increase in the piston speed in the normal speed region where the piston speed is equal to or higher than the second predetermined value is the same as the rate of increase in the damping force on the extension side with respect to an increase in the piston speed in the extremely low speed region where the piston speed is less than the second predetermined value. lower than the rate of increase in force. In other words, the slope of the rate of increase in the damping force on the extension side with respect to the increase in piston speed in the normal speed region can be made slower than in the extremely low speed region.

Of the first damping force generation mechanism 42 and the second damping force generation mechanism 202 shown in FIG. It is more rigid and has a higher opening pressure. Therefore, in the retraction stroke, in an extremely low speed region where the piston speed is lower than a predetermined value, the first damping force generation mechanism 42 is closed and the second damping force generation mechanism 202 is opened, and the piston speed is lower than this predetermined value. In the normal speed range above the value, both the second damping force generation mechanism 202 and the first damping force generation mechanism 42 open. In other words, the first damping force generation mechanism 42 is provided in the compression/discharge side passage 222, and is closed in a region where the piston speed is low, and opened in a speed region where the piston speed is higher than the low speed. Further, the second damping force generation mechanism 202 is provided in the contraction introduction side passage 221, and opens from a region where the piston speed is low. The sub-valve 201 is an extremely low-speed valve that opens in a region where the piston speed is extremely low to generate damping force.

In the contraction stroke, the piston 18 moves toward the lower chamber 20, thereby increasing the pressure in the lower chamber 20 and decreasing the pressure in the upper chamber 19. In the contraction stroke when the piston speed is less than the third predetermined value, the oil L in the lower chamber 20 flows into the upper chamber 19 via the contraction introduction side passage 221 and the contraction discharge side passage 222. The second damping force generation mechanism 202 of the introduction side passage 221 does not open, and the first damping force generation mechanism 42 of the contraction discharge side passage 222 also does not open. Therefore, the oil L in the lower chamber 20 is contained in the communication chamber 207 shown in FIG. , the passage in the passage hole 121, the valve chamber 205, the passage in the passage hole 39, and the passage in the passage groove 51 shown in FIG. This causes the damping force to rise rapidly.

During the contraction stroke when the piston speed is greater than or equal to the third predetermined value and less than the fourth predetermined value, the first damping force generating mechanism 42 of the contraction discharge side passage 222 does not open, and the oil L in the lower chamber 20 is From the communication chamber 207 shown in FIG. and flows into the upper chamber 19.

At this time, the oil L from the communication chamber 207 is introduced into the second valve inner chamber 209 from the passage in the notch 165 of the second coupling disk 107 and the passage hole 166 in the sub-valve 201 . Then, the pressure inside the second valve inner chamber 209 increases, causing the annular disk 105 to bend toward the case chamber 206 and away from the seat portion 114, and also to push the annular disk 105 into contact with the protrusion 152 of the first coupling disk 103. The first coupling disk 103 is bent toward the case chamber 206 and separated from the seat portion 114 . Thereby, in the retraction stroke, even in an extremely low speed region where the piston speed is greater than or equal to the third predetermined value and less than the fourth predetermined value, a damping force having a valve characteristic (a characteristic in which the damping force is substantially proportional to the piston speed) can be obtained.

At this time, the sub-valve 201 is separated from the seat portion 114 by the amount of deformation or movement until the annular disk 105 brings the first coupling disk 103 into contact with the first stopper member 102 and the deformation or movement is restricted. That is, the maximum opening area between the annular disk 105 and the seat portion 114 when the valve is opened to the maximum is different. If the first movement distance adjusting member 104 is thick and the amount of deformation, that is, the amount of movement of the annular disk 105 until the first coupling disk 103 comes into contact with the first stopper member 102 is large, the annular disk 105 and the seat at the maximum valve opening are The maximum opening area between the portions 114 becomes larger, and the generated damping force becomes lower. On the other hand, if the first movement distance adjusting member 104 is thin and the amount of deformation, that is, the amount of movement of the annular disk 105 until the first coupling disk 103 comes into contact with the first stopper member 102 is small, the annular disk 105 at the maximum valve opening is The maximum opening area between the seat portions 114 becomes smaller, and the generated damping force becomes higher.

Further, in the retraction stroke, in a normal speed range where the piston speed is equal to or higher than the fourth predetermined value, the first damping force generating mechanism 42 opens while the second damping force generating mechanism 202 remains open. In other words, the annular disk 105 and the first coupling disk 103 of the sub-valve 201 separate from the seat part 114, and the oil L flows from the lower chamber 20 to the case chamber 206 in the contraction introduction side passage 221. Since the discharge side passage 222 is a passage in the passage groove 51 which is an orifice, and the flow rate of the oil liquid L is restricted, the differential pressure generated in the main valve 71 increases, and the main valve 71 is separated from the valve seat part 50. Then, the oil L flows from the valve chamber 205 to the upper chamber 19 via the contraction discharge side passage 222. As a result, even in the normal speed range where the piston speed is equal to or higher than the fourth predetermined value in the retraction stroke, a damping force having the valve characteristic (the damping force is approximately proportional to the piston speed) can be obtained.

In the retraction stroke, the rate of increase in the damping force on the contraction side with respect to the increase in piston speed in the normal speed region where the piston speed is equal to or higher than the fourth predetermined value is the same as the rate of increase in the damping force on the contraction side with respect to the increase in piston speed in the extremely low speed region where the piston speed is less than the fourth predetermined value. This is lower than the rate of increase in damping force on the compression side. In other words, the slope of the rate of increase in damping force on the compression side with respect to the increase in piston speed in the normal speed region can be made slower than in the extremely low speed region.

In addition, in the compression stroke, the damping force characteristics by the damping valve mechanism 257 are also combined.

The above-mentioned Patent Document 1 discloses a valve that includes a leaf valve that can be bent in both directions in the axial direction, and an annular opposing portion that is provided with a gap between the leaf valve and the free end of the leaf valve. Incidentally, in a cylinder device equipped with such a valve, it is required to adjust the damping force generated by the valve in more detail.

The cylinder device 1 has an extension introduction side passage 211 and a contraction discharge side passage 222 through which the oil L flows out from one of the upper chamber 19 and the lower chamber 20 in the cylinder 2 due to the movement of the piston 18, and an extension introduction side passage. 211 to generate a damping force, a first damping force generating mechanism 42 to be provided to the contraction and discharge side passage 222 to generate a damping force, and a valve device 99. There is.

The valve device 99 includes at least an expansion discharge side passage 212 provided in series with the expansion introduction side passage 211, a contraction introduction side passage 221 provided in series with the contraction discharge side passage 222, and an expansion discharge side passage 212 inside. A cylindrical case member 100 in which at least a part of the contraction introduction side passage 221 is formed, a mounting shaft portion 28 disposed within the case member 100, and a mounting shaft portion 28 that is inserted into the case member 100 by passing through the mounting shaft portion 28. It has an annular disk 105 which is disposed on the inner circumferential side, has a gap between it and the case member 100 on the non-supported side, and can be bent on one axial side and the other axial side. The valve device 99 also includes a first stopper member 102 and a first joint disc 103 that restrict movement of the annular disc 105 on one side in the axial direction, and a second joint disc that restricts movement of the annular disc 105 on the other side in the axial direction. 107 and a second stopper member 108, a first movement distance adjustment member 104 that is provided between the annular disk 105 and the first coupling disk 103 and is capable of adjusting the movement distance on one side in the axial direction of the annular disk 105; A second movement distance adjustment member 106 is provided between the disk 105 and the second coupling disk 107 and is capable of adjusting the movement distance of the annular disk 105 on the other side in the axial direction.

Therefore, by adjusting the movement distance of the annular disk 105 on one side in the axial direction by the first movement distance adjustment member 104, the damping force in the contraction stroke can be adjusted. Further, by adjusting the movement distance of the annular disk 105 on the other side in the axial direction by the second movement distance adjustment member 106, the damping force in the extension stroke can be adjusted. Therefore, in the cylinder device 1, since the valve device 99 can independently adjust the damping force in the extension stroke and the contraction stroke, it becomes possible to adjust the damping force in more detail.

In other words, by increasing the thickness of the disk 101 and decreasing the thickness of the first movement distance adjusting member 104, the movement distance of the annular disk 105 on one side in the axial direction can be reduced, thereby reducing the second damping force in the contraction stroke. The maximum opening area between the annular disk 105 and the seat portion 114 when the generating mechanism 202 is opened can be reduced, and the damping force can be increased. Furthermore, if the distance of movement of the annular disk 105 on one side in the axial direction is increased by reducing the thickness of the disk 101 and increasing the thickness of the first movement distance adjustment member 104, the second damping force in the contraction stroke can be increased. The maximum opening area between the annular disk 105 and the seat portion 114 when the generating mechanism 202 is opened can be increased, and the damping force can be reduced.

Furthermore, by reducing the thickness of the second movement distance adjusting member 106, the movement distance of the annular disk 105 on the other side in the axial direction can be reduced. The maximum opening area between the annular disk 105 and the seat portion 114 can be reduced, and the damping force can be increased. Furthermore, by increasing the thickness of the second movement distance adjusting member 106, the movement distance of the annular disk 105 on the other side in the axial direction can be increased. The maximum opening area between the annular disk 105 and the seat portion 114 can be increased, and the damping force can be reduced.

Therefore, in the cylinder device 1, the damping force characteristics in the extremely low speed region can be set by the valve device 99 independently for the extension stroke and the contraction stroke, so that the damping force can be adjusted in more detail.

Here, in the sub-valve 201, in the initial state, the annular disk 105 is axially aligned with the opposing surface 133 of the seat portion 114, and the opening area between the annular disk 105 and the seat portion 114 is minimized. When the differential pressure generated across the annular disk 105 increases, the sub-valve 201 maintains the minimum opening area between the annular disk 105 and the seat portion 114 for a predetermined distance, and then expands this opening area. The valve device 99 of the cylinder device 1 starts expanding the opening area between the annular disk 105 and the seat portion 114 by adjusting the thickness of the first movement distance adjustment member 104 and the thickness of the second movement distance adjustment member 106. The differential pressure applied can be varied.

For example, in the first pattern in which the thickness of the first movement distance adjustment member 104 and the thickness of the second movement distance adjustment member 106 are equal, as shown by the broken line in FIG. 6, the extension stroke (right side from the origin in FIG. 6) The differential pressure of the annular disk 105 starts to expand the opening area between the annular disk 105 and the seat part 114 at , and the opening area between the annular disk 105 and the seat part 114 starts to expand during the contraction stroke (left side from the origin in FIG. 6). The starting differential pressure of the annular disk 105 can be set to an equivalent value with the positive and negative reversed. Further, in the first pattern, the relationship between the opening area between the annular disk 105 and the seat portion 114 with respect to the increase in the differential pressure of the annular disk 105 can also be made to have the same characteristic with the positive and negative polarities reversed.

As shown by the broken line in FIG. 7, the damping force characteristics in the very low speed region (near 0.005 m/s) suddenly change before the opening area between the annular disk 105 and the seat portion 114 is expanded, where the piston speed is slow. After the increase rate of the damping force with respect to the increase in piston speed increases (the damping force rises rapidly) and the opening area between the annular disk 105 and the seat portion 114 starts to expand, the opening area between the annular disk 105 and the seat portion 114 increases. As , the rate of increase in damping force with respect to increase in piston speed becomes smaller. In the first pattern, the extension stroke and the contraction stroke can have the same characteristics with the positive and negative reversed.

For example, as shown in FIGS. 3 to 5, in a second pattern in which the first moving distance adjusting member 104 is made thicker and the second moving distance adjusting member 106 is thinner, the solid line in FIG. As shown in FIG. 6, the differential pressure of the annular disk 105 that starts to expand the opening area between the annular disk 105 and the seat portion 114 in the extension stroke (right side from the origin in FIG. 6) is increased, and On the left side), the differential pressure of the annular disk 105 can be reduced by increasing the opening area between the annular disk 105 and the seat portion 114.

In addition, in the second pattern, the relationship between the increase in the opening area between the annular disk 105 and the seat portion 114 with respect to the increase in the differential pressure of the annular disk 105 after the opening area starts to expand is as follows: The amount of increase in the differential pressure of the annular disk 105 required for this is greater during the extension stroke than during the contraction stroke.

In the second pattern, as shown by the solid line in FIG. 7, the damping force characteristics in the extremely low speed region of the extension stroke are as follows: The damping force maintains the characteristic of rapidly rising until the piston speed becomes faster than the pattern, and after the opening area between the annular disk 105 and the seat portion 114 starts to expand, the piston speed increases as the opening area increases. Although the increase rate of the damping force against the pattern becomes smaller, it is possible to obtain a higher hard damping force than in the first pattern.

In addition, in the second pattern, the damping force characteristics in the extremely low speed region of the retraction stroke are such that before the opening area between the annular disk 105 and the seat portion 114, where the piston speed is slow, is expanded, the piston speed is slower than in the first pattern. After the opening area between the annular disk 105 and the seat portion 114 starts to expand, the rate of increase in the damping force with respect to the increase in piston speed becomes smaller as the opening area increases. , the damping force becomes softer than that of the first pattern.

In this way, in the second pattern, the damping force characteristics in the extremely low speed region generated by the valve device 99 can be made to differ greatly between the extension stroke and the contraction stroke.

In the valve device 99 of the cylinder device 1, the first moving distance adjusting member 104 and the second moving distance adjusting member 106 have different thicknesses in the axial direction as described above. By adjusting the thickness of the first travel distance adjusting member 104 and the thickness of the second travel distance adjusting member 106 in this way, the valve device 99 can independently adjust the damping force in the extension stroke and the contraction stroke. This makes it possible to easily adjust the damping force.

In the valve device 99 of the cylinder device 1, a protrusion 152 that protrudes toward the annular disk 105 is provided on the first coupling disk 103. Therefore, when the annular disk 105 deforms toward the first coupling disk 103, the annular disk 105 can be brought into contact with the first coupling disk 103 at an early stage to generate a resistance force. Furthermore, a protrusion 162 that protrudes toward the annular disk 105 is provided on the second coupling disk 107 . Therefore, when the annular disk 105 deforms toward the second coupling disk 107, the annular disk 105 can be brought into contact with the second coupling disk 107 at an early stage to generate a resistance force.

In the above embodiment, the inner circumferential side of the annular disk 105 is supported by the mounting shaft portion 28 of the piston rod 21, and the outer circumferential side, which is the non-supported side of the annular disk 105, is attached to the case member with a gap. 100 was set. However, on the contrary, the outer circumferential side of the annular disk 105 is supported by the outer cylindrical portion 112 of the case member 100, and the piston rod 21 is attached to the inner circumferential side of the annular disk 105, which is not supported, with a gap. It is also possible to provide a mounting shaft portion 28 of.

Further, in the above embodiment, the extension discharge side passage 212 in which the second damping force generation mechanism 202 is provided is provided in series with the extension introduction passage 211 in which the first damping force generation mechanism 41 is provided, and the first damping force generation mechanism 41 is A contraction introduction side passage 221 in which the second damping force generation mechanism 202 is provided is provided in series with the contraction discharge side passage 222 in which the generation mechanism 42 is provided. However, for example, the piston 18 and the case member 100 may not be fitted together, the fitting cylinder portion 95 and the passage hole 121 may be eliminated, and the expansion/discharge side passage 212 and the contraction introduction side passage 221 may be provided inside the piston rod 21. By directly opening into the upper chamber 19 through the passage, an extension discharge side passage 212 in which the second damping force generation mechanism 202 is provided is provided in parallel with the extension introduction side passage 211 in which the first damping force generation mechanism 41 is provided, It is also possible to provide a contraction introduction side passage 221 in which the second damping force generation mechanism 202 is provided in parallel with the contraction discharge side passage 222 in which the first damping force generation mechanism 42 is provided.

DESCRIPTION OF SYMBOLS 1... Cylinder device, 2... Cylinder, 18... Piston, 19... Upper chamber, 20... Lower chamber, 21... Piston rod, 28... Mounting shaft part (shaft part), 41... First damping force generation mechanism (damping force generation mechanism), 42...first damping force generation mechanism (damping force generation mechanism), 99...valve device, 100...case member, 102...first stopper member (first movement regulating member), 103...first coupling disk (first 1 movement regulating member), 104... first movement distance adjustment member (first movement distance adjustment means), 105... annular disk, 106... second movement distance adjustment member (second movement distance adjustment means), 107... second coupling Disk (second movement regulating member), 108... Second stopper member (second movement regulating member), 152, 162... Projection, 211... Extension introduction side passage (first passage), 212... Extension discharge side passage (first passage). 2 passage), 221... contraction introduction side passage (second passage), 222... contraction discharge side passage (first passage).

Claims (4)

a cylinder in which a working fluid is sealed;
a piston that is slidably fitted into the cylinder and partitions the inside of the cylinder into two chambers;
a piston rod having one end connected to the piston and the other end extending outside the cylinder;
a first passage through which working fluid flows from one chamber in the cylinder due to movement of the piston;
a second passage provided in series or parallel to the first passage;
a damping force generation mechanism that is provided in the first passage and generates a damping force;
a cylindrical case member in which at least a portion of the second passage is formed;
a shaft portion disposed within the case member;
The shaft is disposed in the case member by passing through the shaft, is supported on the inner peripheral side or the outer peripheral side, has a gap on the non-supported side with the case member or with the shaft, and is aligned in the axial direction. an annular disk deflectable on one side and the other axially;
a first movement regulating member that regulates movement of the annular disk on one side in the axial direction;
a second movement restriction member that restricts movement of the annular disk on the other side in the axial direction;
a first movement distance adjusting means provided between the annular disk and the first movement regulating member and capable of adjusting a movement distance of the annular disk on one side in the axial direction;
a second movement distance adjusting means provided between the annular disk and the second movement regulating member and capable of adjusting the movement distance of the annular disk on the other side in the axial direction;
A cylinder device with The cylinder device according to claim 1, wherein the first moving distance adjusting means and the second moving distance adjusting means have different thicknesses in the axial direction. The cylinder device according to claim 1 or 2, wherein the first movement regulating member and the second movement regulating member are each provided with a protrusion that protrudes toward the annular disk. a cylindrical case member having a passage formed therein;
a shaft portion disposed within the case member;
The shaft is disposed in the case member by passing through the shaft, is supported on the inner peripheral side or the outer peripheral side, has a gap on the non-supported side with the case member or with the shaft, and is aligned in the axial direction. an annular disk deflectable on one side and the other axially;
a first movement regulating member that regulates movement of the annular disk on one side in the axial direction;
a second movement restriction member that restricts movement of the annular disk on the other side in the axial direction;
a first movement distance adjusting means provided between the annular disk and the first movement regulating member and capable of adjusting a movement distance of the annular disk on one side in the axial direction;
a second movement distance adjusting means provided between the annular disk and the second movement regulating member and capable of adjusting the movement distance of the annular disk on the other side in the axial direction;
Valve device with.

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