JP2018132137A - Cylinder device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make a whole cylinder device compact.SOLUTION: A flow path 11 is provided with a step part 11B1 on the side where working fluid flows in when a piston rod 9 moves. A valve mechanism 12 is provided with: a first valve seat 13 provided for the step part 11B1; a first valve body 14 which is inserted in the flow path 11, one side of which is in contact with the first valve seat 13 separably, and which is provided with a valve passage 14C extending in a separation/contact direction; a first spring 16 energizing the first valve body 14 in the direction in which to seat it on the first valve seat 13; a second valve body 17 which is in contact with the first valve body 14 and provided in the way that it can open/close the valve passage 14C; a second spring 18 which energizes the second valve body 17 in the direction in which to bring it in contact with the first valve body 14; a first spring receiver 19 capable of moving in the direction in which to adjust an energizing force of the first spring 16; and a second spring receiver 20 capable of moving in the direction in which to adjust an energizing force of the second spring 18.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a cylinder device for suppressing shaking of a structure such as a railway vehicle or a building.

  2. Description of the Related Art Generally, structures such as railway vehicles and buildings are provided with a cylinder device that uses a working fluid to cushion vibrations. In this cylinder device, a resistance force is applied to the working fluid sealed in the cylinder by a valve mechanism, thereby generating a damping force to alleviate the vibration.

  In this case, the valve mechanism of the cylinder device includes two types of valve mechanisms: a high-speed valve mechanism that opens when the piston rod expands and contracts at high speed, and a low-speed valve mechanism that opens when the piston expands and contracts at low speed. (For example, refer to Patent Document 1).

JP 2014-167335 A

  By the way, since the cylinder apparatus by patent document 1 has two types of valve mechanisms, since the space for installing two valve mechanisms is needed, it becomes an obstacle at the time of size reduction of a cylinder apparatus. There is a problem.

  The present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to provide a cylinder device that can be miniaturized as a whole.

  The present invention includes a cylinder in which a working fluid is sealed, a partition member that is fitted in the cylinder and divides the inside of the cylinder into at least two chambers, and a piston rod that has a tip extending outside the cylinder. A cylinder device provided in the partition member and having a flow path that allows the working fluid to flow between the two chambers and a valve mechanism that is provided in the flow path and generates a damping force. The flow passage is provided with a step portion formed toward the radially inner side of the flow passage on the side where the working fluid flows when the piston rod moves, and the valve mechanism is disposed on the step portion. A first valve body, a first valve body that is inserted into the flow path, has one side detachably contacting the first valve seat, and provided with a valve passage extending in the separation direction; One end abuts against the other side of the one valve body, and the first valve body is connected to the first valve. A first urging member that urges in a direction to be seated on the first valve body, a second valve body that is in contact with the first valve body from the other side of the first valve body, and that can open and close the valve passage; A second urging member for urging the second valve body in a direction to abut against the other side of the second valve body and causing the second valve body to abut against the first valve body; and the other side of the first urging member And a first spring receiver that is movable in a direction to adjust the urging force of the first urging member, and abuts with the other side of the second urging member, and the urging force of the second urging member is reduced. A second spring receiver that is movable in the adjusting direction.

  According to the present invention, the entire cylinder device can be reduced in size.

It is a longitudinal section showing a cylinder device by a 1st embodiment of the present invention. It is a longitudinal cross-sectional view which expands and shows the II section in FIG. It is the side view which expanded the single 2nd valve body from the side, and was seen. It is a top view of the 2nd valve body shown in FIG. It is a longitudinal cross-sectional view which shows the cylinder apparatus by the 2nd Embodiment of this invention. It is the right view which looked at the piston and each valve mechanism from the arrow VI-VI direction in FIG. It is an expanded sectional view which expands and shows the principal part in FIG. It is a characteristic diagram which shows the relationship between the displacement speed of a piston, and damping force. It is the longitudinal cross-sectional view which looked at the valve mechanism by the 3rd Embodiment of this invention from the same position as FIG.

  Hereinafter, a cylinder device according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings, taking as an example the case of applying to a hydraulic shock absorber.

  1 and 4 show a first embodiment of the present invention. In the first embodiment, a case where a hydraulic shock absorber is used to reduce vibration of a railway vehicle is illustrated.

  In FIG. 1, a hydraulic shock absorber 1 constituting a cylinder device includes a cylindrical outer cylinder 2, an inner cylinder 6, a piston 8, a piston rod 9, a rod guide 10, a flow path 11, and a valve mechanism 12 that form an outer shell. It is configured to include. The hydraulic shock absorber 1 is mounted in a horizontally placed state, for example, between a railway vehicle body and a bogie (both not shown).

  The outer cylinder 2 of the hydraulic shock absorber 1 constitutes a cylinder together with the inner cylinder 6. The outer cylinder 2 is located on the outer peripheral side of the inner cylinder 6 and is provided coaxially with the inner cylinder 6. One end side of the outer cylinder 2 (the left end side of the outer cylinder 2 shown in FIG. 1) is closed by the bottom cap 3, and the other end side (the right end side of the outer cylinder 2 shown in FIG. 1) is closed by a rod guide 10 described later. It is blocked. A cylindrical cover 4 that covers a piston rod 9 described later is attached to the other end of the outer cylinder 2. Here, the bottom cap 3 is provided with, for example, an attachment eye 5A attached to the body or carriage of the railway vehicle, and the cylindrical cover 4 is provided with an attachment eye 5B attached to the carriage or body of the railway vehicle. .

  The inner cylinder 6 of the hydraulic shock absorber 1 constitutes a cylinder together with the outer cylinder 2, and is provided coaxially within the outer cylinder 2. One end side of the inner cylinder 6 is fitted to the bottom cap 3 side via a bottom valve 7. The other end side of the inner cylinder 6 is fitted in the fitting recess 10 </ b> A of the rod guide 10. A working fluid as a working fluid is sealed in the inner cylinder 6. The working fluid is not limited to hydraulic oil or oil, and for example, water mixed with additives can be used.

  In this case, an annular reservoir chamber A is formed between the inner cylinder 6 and the outer cylinder 2, and gas is sealed in the reservoir chamber A together with the hydraulic fluid. In the reservoir chamber A, the liquid level of the hydraulic fluid is set so that a later-described valve mechanism 12 is always located in the hydraulic fluid. The gas sealed in the reservoir chamber A may be air at atmospheric pressure, or a gas such as compressed nitrogen gas may be used. The gas in the reservoir chamber A is compressed to compensate for the entry volume of the piston rod 9 during the reduction stroke of the piston rod 9.

  The bottom valve 7 is located on one end side of the inner cylinder 6 and is provided between the bottom cap 3 and the inner cylinder 6. The bottom valve 7 has a suction valve 7A as a bottom side valve that allows the working fluid in the reservoir chamber A to flow toward the bottom side oil chamber C in the inner cylinder 6 and prevents reverse flow. Is provided.

  Here, the suction valve 7A keeps the inner cylinder 6 always filled with the hydraulic fluid when the piston 8 slides and displaces in the inner cylinder 6 to the other side in the axial direction (the rod extension side). To open and close. That is, when the piston 8 slides and displaces in the inner cylinder 6 in the direction of the rod side oil chamber B in the extension stroke of the piston rod 9, the suction valve 7A is opened and the hydraulic fluid in the reservoir chamber A is transferred to the bottom side oil chamber C. It is sucked into.

  The piston 8 constitutes one of partition members slidably inserted (inserted) into the inner cylinder 6. The piston 8 divides the inside of the inner cylinder 6 into two pressure chambers, a bottom side oil chamber C as a chamber on one side and a rod side oil chamber B as a chamber on the other side. The piston 8 is provided with a check valve 8A as a piston side valve that allows the working fluid to flow from the bottom side oil chamber C to the rod side oil chamber B and prevents a reverse flow.

  Here, the check valve 8A opens when the piston 8 is slidably displaced in the direction of reducing the bottom side oil chamber C in the inner cylinder 6 during the reduction stroke of the piston rod 9. Thereby, the check valve 8 </ b> A can cause the working fluid in the bottom side oil chamber C to flow to the rod side oil chamber B.

  The piston rod 9 is connected to the piston 8 in the inner cylinder 6 on the base end side. On the other hand, the tip end side (projection end side) of the piston rod 9 projects so as to extend and contract so as to extend to the outside of the inner cylinder 6 via the rod guide 10 and the like. The tip end side of the piston rod 9 is attached to, for example, a carriage of a railway vehicle via an attachment eye 5B.

  The rod guide 10 is inserted into the outer cylinder 2 and constitutes a partition member that partitions the inside of the outer cylinder 2 (inner cylinder 6) into a reservoir chamber A and a rod-side oil chamber B. The rod guide 10 is formed as a thick stepped cylindrical body, and a fitting recess 10A into which the inner cylinder 6 is fitted is formed on one side portion of the inner diameter side thereof. The rod guide 10 positions the inner cylinder 6 at the center of the outer cylinder 2 in the radial direction by fitting the other side portion of the inner cylinder 6 into the fitting recess 10 </ b> A. On this basis, the rod guide 10 guides (guides) the piston rod 9 so as to be slidable in the axial direction by the inner peripheral surface 10B. Furthermore, the outer peripheral surface 10C of the rod guide 10 is fitted in the outer cylinder 2 in a gas-liquid tight state. Here, the rod guide 10 is provided with a flow path 11 through which hydraulic fluid flows by sliding displacement of a piston 8 inserted into the inner cylinder 6.

  The flow path 11 is provided in the rod guide 10 and allows the hydraulic fluid to flow through the reservoir chamber A and the rod-side oil chamber B in communication. As shown in FIG. 2, the flow path 11 is located on the inner diameter side of the rod guide 10 and extends in the axial direction along the piston rod 9, and its upstream side communicates with the rod side oil chamber B, and the downstream side is in the radial direction. An L-shaped inflow passage 11A bent outward, a valve housing chamber 11B communicating with the downstream side of the inflow passage 11A and extending in the radial direction of the rod guide 10, and a shaft positioned on the outer diameter side of the rod guide 10 The outlet passage 11C extends in the direction and communicates the valve storage chamber 11B and the reservoir chamber A. The flow path 11 is provided at a position on the lower side of the rod guide 10 in the upper and lower directions, and the flow path 11 is always filled with the working fluid.

  The valve accommodating chamber 11 </ b> B of the flow path 11 is formed as a stepped cylindrical space whose axial line is the radial direction of the rod guide 10. On the upstream side of the valve accommodating chamber 11B on the side into which the hydraulic fluid flows, a step portion 11B1 formed toward the radially inner side of the inflow passage 11A is provided. The step portion 11B1 forms the bottom surface of the valve accommodating chamber 11B, and is formed as, for example, a circular flat surface. On this basis, a portion closer to the center of the step portion 11B1 (around the communicating portion of the inflow passage 11A) is a first valve seat 13 to which a distal end surface 14A of the first valve body 14 described later is separated.

  The valve storage chamber 11B has a slightly larger inner diameter than a first spring 16 described later. Thereby, the valve accommodating chamber 11 </ b> B can guide the first valve body 14 so that the first valve body 14 is accurately attached to and detached from the first valve seat 13.

  A female screw 11B2 is formed on the downstream side of the valve accommodating chamber 11B (the outer diameter side of the rod guide 10). A first outer screw 19A of a first spring receiver 19 described later is screwed into the female screw 11B2. Furthermore, a communication space 11B3 is formed between the outer cylinder 2 and the valve accommodating chamber 11B, which is located on the outer diameter side of the rod guide 10 with respect to the female screw 11B2. The communication space 11B3 communicates with the upstream side of the outflow passage 11C.

  Next, the configuration and operation of the valve mechanism 12 which is a characteristic part of the present invention will be described.

  The valve mechanism 12 is provided in the flow path 11. The valve mechanism 12 generates a damping force by applying resistance to the hydraulic fluid flowing through the flow path 11 when the piston rod 9 expands and contracts. The valve mechanism 12 includes a first valve seat 13, a first valve body 14, a second valve seat 15, a first spring 16, a second valve body 17, a second spring 18, a first spring receiver 19, and a second spring, which will be described later. The receiver 20 is configured to be included. Here, the valve mechanism 12 is opened when the displacement speed of the piston 8 is high and a large amount of hydraulic fluid flows at a stroke, and the valve mechanism 12 opens only when a small amount of hydraulic fluid flows due to the low displacement speed of the piston 8. And a second valve body 17.

  The first valve seat 13 is provided around the central portion of the step portion 11B1 of the valve accommodating chamber 11B, that is, around the portion where the inflow passage 11A communicates. The first valve seat 13 is formed as an annular flat surface on which the distal end surface 14A of the first valve body 14 is separated (contacted or separated).

  The first valve element 14 is inserted into the valve accommodating chamber 11B of the flow path 11 as a main valve element. The first valve body 14 is formed as a stepped cylindrical body having a conical shape in which the distal end side facing the step portion 11B1 is reduced in diameter toward the step portion 11B1 and the proximal end side is reduced in diameter. As for the 1st valve body 14, the front end side used as one side is the flat front end surface 14A which contacts the 1st valve seat 13 so that isolation | separation is possible. Further, on the other side of the outer peripheral side of the first valve body 14, a spring contact portion 14 </ b> B with which one end of a first spring 16 described later contacts is formed. Further, the first valve body 14 has a valve passage 14C that extends in the separation / contact direction (the axial direction of the first valve body 14) at the axial center position and penetrates with a smaller passage area than the inflow passage 11A. Here, as for the 1st valve body 14, the end surface of the other side used as 14 A of front end surfaces and an axial direction is the 2nd valve seat 15 mentioned later.

  The second valve seat 15 is provided on the other end face of the first valve body 14. The second valve seat 15 contacts and separates the contact surface 17A of the second valve body 17, and is formed as an annular flat surface surrounding the valve passage 14C.

  The first spring 16 as the first biasing member is formed as a compression coil spring, for example. The first spring 16 has one end in the expansion / contraction direction in contact with the spring contact portion 14B located on the other side of the first valve body 14, and the other end in the expansion / contraction direction contacts the contact surface 19B of the first spring receiver 19. ing. As a result, the first spring 16 biases the first valve body 14 in the direction in which the first valve body 14 is seated on the first valve seat 13. The first spring 16 has a larger urging force (spring force) than the second spring 18 described later. Thereby, the first valve body 14 biased by the first spring 16 has a pressure larger than the pressure (pressure difference between the reservoir chamber A and the rod side oil chamber B) when the second valve body 17 is opened. It opens when it acts.

  The second valve body 17 is a sub valve body that opens and closes the valve passage 14 </ b> C of the first valve body 14, and is inserted into the valve accommodating chamber 11 </ b> B of the flow path 11 together with the first valve body 14. Specifically, the second valve body 17 is arranged coaxially so as to be continuous with the proximal end side of the first valve body 14. The second valve body 17 opens when the displacement speed of the piston 8 is slow and a small amount of hydraulic oil flows through the flow path 11.

  The second valve body 17 is formed as a stepped cylinder having a large diameter at the distal end facing the proximal end surface 14D of the first valve body 14 and a small diameter at the proximal end. As for the 2nd valve body 17, the front end side used as one side becomes the contact surface 17A which contact | abuts to the 2nd valve seat 15 so that separation / contact is possible. On the outer peripheral side of the second valve body 17, a spring contact portion 17B with which one end of a second spring 18 described later contacts is formed. Further, the second valve body 17 has a base end surface 17C that is flat on the opposite side of the contact surface 17A in the axial direction.

  Further, a guide shaft portion 17D that protrudes from the contact surface 17A toward the inside of the valve passage 14C is provided at the distal end portion of the second valve body 17. The guide shaft portion 17D guides the opening / closing operation of the second valve body 17. In this case, as shown in FIGS. 3 and 4, a plurality of, for example, two axial grooves 17E extend in the axial direction in the guide shaft portion 17D in order to circulate the working fluid in the valve passage 14C. Is provided. And when the 2nd valve body 17 opens, it can distribute | circulate a hydraulic fluid smoothly, making each axial direction groove part 17E act as a throttle part. The shape and the number of the axial grooves 17E are set according to various conditions, and one or three or more may be provided in addition to the two described above.

  Similar to the first spring 16, the second spring 18 as the second urging member is formed as a compression coil spring. The second spring 18 has one end in the expansion / contraction direction in contact with the spring contact portion 17 </ b> B of the second valve body 17, and the other end in the expansion / contraction direction is in contact with the second spring receiver 20. As a result, the second spring 18 biases the second valve body 17 in the direction in which the second valve body 17 is seated on the second valve seat 15. The second spring 18 has a smaller urging force (spring force) than the first spring 16. As a result, the second valve body 17 biased by the second spring 18 is opened only by a pressure smaller than the pressure when the first valve body 14 is opened.

  The first spring receiver 19 is in contact with the other end of the first spring 16 and adjusts the urging force of the first spring 16. The first spring receiver 19 is disposed on the proximal end side in the valve accommodating chamber 11 </ b> B of the flow path 11 so as to face the first valve body 14, and the first spring 16 is sandwiched between the first valve body 14. . The first spring receiver 19 is formed as a cylindrical body, and a first outer screw 19A is formed on the outer peripheral portion. The first outer screw 19A is screwed into the female screw 11B2 of the valve accommodating chamber 11B. Thereby, the 1st spring receiver 19 can move to the direction which can adjust the axial direction dimension of the 1st spring 16, ie, the spring force of the 1st spring 16, by rotating in arbitrary directions. Further, the first spring receiver 19 has a first inner screw 19 </ b> C on an inner peripheral portion sandwiching a contact surface 19 </ b> B with the first spring 16. The second outer screw 20A of the second spring receiver 20 is screwed into the first inner screw 19C.

  The second spring receiver 20 is in contact with the other end of the second spring 18 and adjusts the urging force of the second spring 18. The second spring receiver 20 is disposed on the inner peripheral side of the first spring receiver 19 so as to face the second valve body 17, and the second spring 18 is sandwiched between the second spring receiver 20 and the second valve body 17. The second spring receiver 20 is formed as a stepped cylindrical body, and a second outer screw 20A is formed on the outer peripheral portion. The second outer screw 20 </ b> A is screwed to the first inner screw 19 </ b> C of the first spring receiver 19. Thereby, the 2nd spring receiver 20 can move to the direction which can adjust the axial direction dimension of the 2nd spring 18, ie, the spring force of the 2nd spring 18, by rotating in arbitrary directions.

  The second spring receiver 20 has a contact surface 20B on the second valve body 17 side, and protrudes from the inner peripheral side of the contact surface 20B toward the second valve body 17 to form a protruding cylinder 20C. . The inside of the protruding cylinder 20C is an outflow path 20D that penetrates in the axial direction and allows the hydraulic fluid to flow out. Here, the protruding cylinder 20 </ b> C serves as a stopper that holds the second spring 18 from the inner peripheral side and restricts the amount of movement of the second valve body 17.

  The valve mechanism 12 is configured as described above. Next, an example of a procedure for assembling the valve mechanism 12 in the valve accommodating chamber 11B of the flow path 11 will be described with reference to FIG.

  Before the rod guide 10 is assembled in the outer cylinder 2, the first valve body 14 and the first spring 16 are sequentially inserted into the valve accommodating chamber 11B of the flow path 11 from the outside in the radial direction, and the first spring The first outer screw 19A of the receiver 19 is screwed into the female screw 11B2 of the valve accommodating chamber 11B. At this time, the spring force of the first spring 16 can be adjusted to an appropriate value by managing the screwing position (tightening dimension) of the first spring receiver 19 and the torque at the time of tightening.

  After the first valve body 14, the first spring 16, and the first spring receiver 19 are assembled in the valve storage chamber 11B, the second valve body 17, the second spring 18 and the second spring receiver 20 are assembled. In this case, the second valve body 17 and the second spring 18 are disposed in the first spring 16 through the first spring receiver 19, and the guide shaft portion 17 </ b> D of the second valve body 17 is connected to the valve of the first valve body 14. The second spring 18 is brought into contact with the spring contact portion 17B of the second valve body 17 through the passage 14C. Next, the second outer screw 20 </ b> A of the second spring receiver 20 is screwed into the first inner screw 19 </ b> C of the first spring receiver 19 while the protruding cylinder 20 </ b> C is inserted into the second spring 18. At this time, similarly to the first spring receiver 19 described above, by controlling the screwing position (tightening dimension) of the second spring receiver 20, the torque at the time of tightening, etc., the spring force of the second spring 18 is appropriately adjusted. Can be adjusted to the value.

  The hydraulic shock absorber 1 according to the present embodiment has the above-described configuration, and the operation thereof will be described next.

  In the hydraulic shock absorber 1, a mounting eye 5 </ b> A of the bottom cap 3 located on one end side thereof is attached to, for example, a vehicle body of a railway vehicle. Further, an attachment eye 5B on the other end side of the piston rod 9 is attached to, for example, a carriage of a railway vehicle. Accordingly, the piston rod 9 can be buffered so as to attenuate the vibration of the railway vehicle by extending in the axial direction from the inner cylinder 6 or contracting in the axial direction into the inner cylinder 6.

  When the piston 8 is displaced in the axial direction at a low speed during the extension stroke of the piston rod 9, the pressure difference between the rod side oil chamber B and the reservoir chamber A is small. The flow rate of the working fluid flowing through is small. For this reason, in the valve mechanism 12, the second valve body 17 opens against the second spring 18 having a small spring force. Thereby, the second valve body 17 urged in the closing direction by the second spring 18 can apply a damping force to the hydraulic fluid flowing from the rod side oil chamber B toward the reservoir chamber A, and the piston rod 9 can be buffered so as to suppress the extension operation.

  Further, when the piston 8 is displaced in the axial direction at a high speed during the extension stroke of the piston rod 9, the pressure difference between the rod side oil chamber B and the reservoir chamber A becomes large. The flow rate of the hydraulic fluid flowing into the reservoir chamber A also increases. For this reason, in the valve mechanism 12, in addition to the second valve body 17, the first valve body 14 opens against the first spring 16 having a large spring force. Thereby, a larger damping force can be applied to the hydraulic fluid flowing from the rod-side oil chamber B toward the reservoir chamber A by the first valve body 14 and the second valve body 17, and the extension operation of the piston rod 9 can be suppressed. Can be buffered.

  On the other hand, when the piston rod 9 is in the reduction stroke, the inside of the bottom side oil chamber C is in a high pressure state, so that the working fluid in the bottom side oil chamber C passes through the check valve 8A provided in the piston 8. It flows into the rod side oil chamber B. In this case, the suction valve 7A provided in the bottom valve 7 allows the working fluid in the reservoir chamber A to flow to the bottom side oil chamber C in the inner cylinder 6 and prevents the reverse flow. The hydraulic fluid does not flow from the side oil chamber C into the reservoir chamber A.

  When the pressure difference between the rod-side oil chamber B and the reservoir chamber A increases due to the increase in the entry volume of the piston rod 9, the first valve body 14 and the second valve of the valve mechanism 12 are the same as in the extension stroke described above. The body 17 is appropriately opened, and the hydraulic fluid in the rod side oil chamber B flows from the flow path 11 toward the reservoir chamber A. Thereby, it can buffer so that the reduction operation of the piston rod 9 may be suppressed by the valve mechanism 12.

  Here, the hydraulic shock absorber 1 has a uniflow structure. That is, the hydraulic fluid in the inner cylinder 6 always flows in one direction from the rod side oil chamber B to the reservoir chamber A through the flow path 11 in both the expansion stroke and the reduction stroke of the piston rod 9. . Thereby, if the movement distance in the axial direction of the piston 8 is the same, the same amount of hydraulic fluid passes through the valve mechanism 12 from the rod-side oil chamber B, and therefore the same damping force is generated.

  Thus, according to the present embodiment, the flow path 11 of the rod guide 10 is formed toward the inside in the radial direction of the flow path 11 on the side into which the hydraulic fluid flows when the piston rod 9 moves. A step portion 11B1 of the valve storage chamber 11B is provided. On this, the valve mechanism 12 provided in the flow path 11 is inserted into the first valve seat 13 provided in the step portion 11B1 and the flow path 11, and one side comes into contact with the first valve seat 13 so as to be detachable, The first valve body 14 provided with the valve passage 14C extending in the separation / contact direction, and one end abuts on the other side of the first valve body 14 to attach the first valve body 14 to the first valve seat 13. The first spring 16 that is energized, the second valve body 17 provided so that one side from the other side of the first valve body 14 contacts the first valve body 14 and the valve passage 14C can be opened and closed, and the second valve body 17 One end abuts against the other side and a second spring 18 that urges the second valve body 17 in a direction to abut against the first valve body 14 and a second spring 18 abuts against the other side of the first spring 16. The first spring receiver 19 that can move in the direction of adjusting the urging force of the second spring 18 is in contact with the other side of the second spring 18 and can move in the direction of adjusting the urging force of the second spring 18. It includes a second spring bearing 20.

  Therefore, the valve mechanism 12 has a first valve body 14 that opens when the displacement speed of the piston 8 is fast and a large amount of hydraulic fluid flows, and a first mechanism that opens when a small amount of hydraulic fluid flows because the displacement speed of the piston 8 is slow. Both the two valve bodies 17 can be provided. This eliminates the need to separately assemble the high-speed and low-speed valve bodies on the rod guide 10.

  As a result, the rod guide 10 only needs to be provided with one valve accommodating chamber 11B corresponding to one valve element (valve mechanism 12), so that the number of processing steps for the rod guide 10 can be reduced. . Moreover, since the first valve body 14 and the second valve body 17 can be assembled as a module in the valve mechanism 12, the space for installing the first valve body 14 and the second valve body 17 can be reduced. Therefore, the entire hydraulic shock absorber 1 can be reduced in size.

  The first spring receiver 19 is provided with a first outer screw 19 </ b> A that is screwed into a female screw 11 </ b> B <b> 2 provided on the inner peripheral portion of the valve accommodating chamber 11 </ b> B of the flow path 11 at the outer peripheral portion that forms a cylindrical body. A first inner screw 19C is provided on the periphery. On the other hand, the second spring receiver 20 is provided with a second outer screw 20A that engages with the first inner screw 19C on the outer periphery. Thus, by managing the screwing positions (tightening dimensions) of the first spring receiver 19 and the second spring receiver 20, the torque at the time of tightening, etc., the spring force of the first spring 16 and the second spring 18 is set to an appropriate value. Can be adjusted.

  Next, FIGS. 5 to 8 show a second embodiment of the present invention. The feature of this embodiment is that a plurality of valve mechanisms are provided on the partition member. In addition, in this Embodiment, the case where a cylinder apparatus is attached between a pair of pillar which comprises a building is illustrated, for example. Further, in the present embodiment, of the reduction side and extension side valve mechanisms, the reduction side valve mechanism will be described, and the extension side valve mechanism having the same configuration as the reduction side valve mechanism will be described. Shall be omitted.

  In FIG. 5, a hydraulic shock absorber 31 constituting the cylinder device is called, for example, a vibration damper (vibration damper), and can suppress shaking acting on the building. The hydraulic shock absorber 31 is disposed between a pair of adjacent columns (none of which are shown) among a plurality of columns that support the building. The hydraulic shock absorber 31 includes a cylinder 32, a piston 35, a reduction side channel 36, an extension side channel 37, a piston rod 38, a reduction side valve mechanism 40, and an extension side valve mechanism 49.

  The cylinder 32 is formed as a cylindrical body. In the cylinder 32, a one-side rod guide 33 is provided on one side in the axial direction (left side in FIG. 5). In addition, an other side rod guide 34 is provided on the other side in the cylinder 32 in the axial direction (the right side in FIG. 5). One end of the cylinder 32 is attached to one pillar constituting the building via an attachment member (not shown). A working fluid as a working fluid is sealed in the cylinder 32. The working fluid is not limited to hydraulic oil or oil, and for example, water mixed with additives can be used.

  The piston 35 constitutes a partition member that is slidably inserted (inserted) into the cylinder 32. The piston 35 divides the inside of the cylinder 32 into two pressure chambers, a one-side oil chamber D as a one-side chamber and an other-side oil chamber E as another-side chamber. The piston 35 is formed as a thick cylindrical body in the axial direction.

  Here, as shown in FIG. 6, the piston 35 is provided with a plurality of, for example, four reduction-side flow paths 36 and four extension-side flow paths 37 penetrating in the axial direction at intervals in the circumferential direction. Yes. In each reduction side flow path 36, the working fluid flows when the piston 35 is displaced to the reduction side of the piston rod 38. On the other hand, in each extension side channel 37, when the piston 35 is displaced to the extension side of the piston rod 38, the working fluid flows. For example, the reduction-side flow paths 36 and the expansion-side flow paths 37 are alternately arranged in the circumferential direction.

  The reduction-side channel 36 and the extension-side channel 37 have the same passage shape that is inverted in the axial direction. Therefore, in the present embodiment, the shape of the reduction-side flow path 36 will be described, and the extension-side flow path 37 will be denoted by reference numerals corresponding to those of the reduction-side flow paths 36, and description thereof will be omitted.

  The reduced-side flow path 36 as a flow path allows the hydraulic fluid to flow through the one-side oil chamber D and the other-side oil chamber E in communication. As shown in FIG. 7, the reduction-side flow path 36 communicates with the one-side oil chamber D and opens into the other-side oil chamber E while communicating with the inflow passage 36 </ b> A in which the piston 35 extends in the axial direction. Thus, the piston 35 is configured by a valve accommodating chamber 36B extending in the axial direction.

  The valve storage chamber 36 </ b> B is formed as a cylindrical space whose axial line is the axial direction of the piston 35. On the upstream side of the valve accommodating chamber 36B, which is the side into which the hydraulic fluid flows, is provided with a step portion 36B1 formed toward the radially inner side of the inflow passage 36A. The step portion 36B1 forms the bottom surface of the valve accommodating chamber 36B, and is formed as, for example, a circular flat surface. In addition, a portion closer to the center of the step portion 36B1 (around the communication portion of the inflow passage 36A) serves as a first valve seat 41 to which a distal end surface 42A of the first valve body 42 described later is separated.

  The valve storage chamber 36 </ b> B has a slightly larger inner diameter than a first spring 44 described later. Thereby, the valve accommodating chamber 36 </ b> B can guide the first valve body 42 so that the first valve body 42 is accurately attached to and detached from the first valve seat 41. A female screw 36B2 is formed on the downstream side (opening side) of the valve housing chamber 36B. A first outer screw 47A of a first spring receiver 47, which will be described later, is screwed into the female screw 36B2.

  Similar to the reduction-side flow path 36, the expansion-side flow path 37 as a flow path is configured by an inflow passage 37A and a valve accommodating chamber 37B having a stepped portion 37B1 and a female screw 37B2.

  As shown in FIG. 5, the piston rod 38 is connected to the piston 35 in the cylinder 32 on the base end side. On the other hand, the front end side (projecting end side) of the piston rod 38 projects so as to extend and contract so as to extend to the outside of the cylinder 32 through the other side rod guide 34. The tip end side of the piston rod 38 is attached to the other pillar (not shown) constituting the building via an attachment member (not shown).

  On the base end side of the piston rod 38, a reduced diameter portion 38A to be inserted into the piston 35 is formed, and an extension rod 38B for fixing the piston 35, for example, is attached to the distal end of the reduced diameter portion 38A. Yes. The extension rod 38 </ b> B is supported by the one-side rod guide 33, whereby the piston rod 38 is supported by the one-side rod guide 33 and the other-side rod guide 34 in a both-sided manner with the piston 35 interposed therebetween.

  The reservoir tank 39 has a reservoir chamber (not shown) communicating with the one-side oil chamber D and the other-side oil chamber E. A gas is sealed in the reservoir chamber together with the working fluid. This gas may be atmospheric pressure air or a compressed gas such as nitrogen gas. The gas in the reservoir chamber absorbs expansion and contraction that occur in the hydraulic fluid due to temperature changes.

  Next, the configuration and operation of the reduction-side valve mechanism 40 and the expansion-side valve mechanism 49, which are features of the present invention, will be described. The reduction side valve mechanism 40 and the extension side valve mechanism 49 use the same parts, and only the assembly direction is opposite in the axial direction. Therefore, in the present embodiment, only the configuration of the reduction side valve mechanism 40 will be described, and the extension side valve mechanism 49 will be denoted by the same reference numerals as the parts of the reduction side valve mechanism 40, and description thereof will be omitted.

  The reduction side valve mechanism 40 as a valve mechanism is provided in each reduction side flow path 36. The reduction side valve mechanism 40 generates a damping force by applying resistance to the working fluid flowing through each reduction side flow path 36 when the piston rod 38 is reduced. The reduction-side valve mechanism 40 includes a first valve seat 41, a first valve body 42, a second valve seat 43, a first spring 44, a second valve body 45, a second spring 46, a first spring receiver 47, a first valve seat 41, which will be described later. Two spring receivers 48 are included. Here, the reduction-side valve mechanism 40 has a first valve element 42 that opens when the displacement speed of the piston 35 is high and a large amount of hydraulic oil flows at a stroke, and a small amount of hydraulic oil flows when the displacement speed of the piston 35 is low. And a second valve body 45 that opens to the rear.

  The first valve seat 41 is provided near the center of the stepped portion 36B1 that forms the valve accommodating chamber 36B of the reduction side flow path 36, that is, around the portion where the inflow passage 36A communicates. The first valve seat 41 is formed as an annular flat surface on which the front end surface 42A of the first valve body 42 is separated (contacted).

  The first valve body 42 is inserted as a main valve body into the valve accommodating chamber 36 </ b> B of the reduction side flow path 36. The first valve body 42 is formed as a stepped cylindrical body having a conical shape in which the distal end side facing the stepped portion 36B1 is reduced in diameter toward the stepped portion 36B1, and the proximal end side is reduced in diameter. As for the 1st valve body 42, the front end side used as one side becomes the flat front end surface 42A which contacts the 1st valve seat 41 so that isolation | separation is possible. Further, on the outer peripheral side of the first valve body 42, a spring contact portion 42 </ b> B with which one end of a first spring 44 described later contacts is formed. Further, the first valve body 42 has a valve passage 42C that extends in the separation / contact direction (the axial direction of the first valve body 42) at the axial center position and penetrates with a smaller passage area than the inflow passage 36A. Here, as for the 1st valve body 42, the end surface of the other side used as the other side of the front end surface 42A and an axial direction is the 2nd valve seat 43 mentioned later.

  The second valve seat 43 is provided on the other end surface of the first valve body 42. The second valve seat 43 is configured so that the contact surface 45A of the second valve body 45 comes into contact with and is formed as an annular flat surface surrounding the valve passage 42C.

  The first spring 44 as the first biasing member is formed as a compression coil spring, for example. The first spring 44 has one end in the expansion / contraction direction in contact with the spring contact portion 42B located on the other side of the first valve body 42, and the other end in the expansion / contraction direction contacts the contact surface 47B of the first spring receiver 47. ing. As a result, the first spring 44 biases the first valve body 42 in the direction (closing direction) in which the first valve body 42 is seated on the first valve seat 41. The first spring 44 has a larger urging force (spring force) than a second spring 46 described later. Accordingly, the first valve body 42 biased by the first spring 44 is larger than the pressure when the second valve body 45 is opened (pressure difference between the one-side oil chamber D and the other-side oil chamber E). It opens when pressure is applied.

  The second valve body 45 is a sub-valve body that opens and closes the valve passage 42 </ b> C of the first valve body 42, and is inserted into the valve accommodating chamber 36 </ b> B of the reduction side flow path 36 together with the first valve body 42. Specifically, the second valve body 45 is arranged coaxially so as to be continuous with the proximal end side of the first valve body 42. The second valve body 45 opens when a small amount of hydraulic fluid flows through the reduction-side flow path 36 because the displacement speed of the piston 35 is slow.

  The second valve body 45 is formed as a stepped cylinder having a large diameter at the distal end facing the proximal end surface 42D of the first valve body 42 and a small diameter at the proximal end. As for the 2nd valve body 45, the front end side used as one side becomes the contact surface 45A which contact | abuts to the 2nd valve seat 43 so that separation / contact is possible. On the outer peripheral side of the second valve body 45, a spring contact portion 45B with which the other end of a second spring 46 described later contacts is formed. The second valve body 45 has a base end surface 45C that is flat on the opposite side of the contact surface 45A in the axial direction.

  Furthermore, a guide shaft portion 45D protruding from the contact surface 45A toward the inside of the valve passage 42C is provided at the distal end portion of the second valve body 45. The guide shaft portion 45D guides the opening / closing operation of the second valve body 45. In this case, the guide shaft portion 45D is provided with, for example, two axial groove portions 45E extending in the axial direction in order to distribute the working fluid in the valve passage 42C. And when the 2nd valve body 45 opens, it can distribute | circulate a hydraulic fluid smoothly, making each axial direction groove part 45E act as a throttle part. The shape and number of the axial grooves 45E are set according to various conditions, and one or three or more may be provided in addition to the two described above.

  Similar to the first spring 44, the second spring 46 as the second urging member is formed as a compression coil spring. The second spring 46 has one end in the expansion / contraction direction in contact with the spring contact portion 45 </ b> B of the second valve body 45, and the other end in the expansion / contraction direction is in contact with the second spring receiver 48. As a result, the second spring 46 biases the second valve body 45 in the direction in which the second valve body 45 is seated on the second valve seat 43 (the valve closing direction). The second spring 46 has a smaller urging force (spring force) than the first spring 44. Thereby, the 2nd valve body 45 currently urged | biased by the 2nd spring 46 can be opened when a pressure smaller than the pressure when the 1st valve body 42 opens is acted.

  The first spring receiver 47 is in contact with the other side of the first spring 44 and adjusts the urging force of the first spring 44. The first spring receiver 47 is disposed on the proximal end side in the valve accommodating chamber 36 </ b> B of the reduction side flow path 36 so as to face the first valve body 42, and the first spring 44 is sandwiched between the first spring body 42. It is out. The first spring receiver 47 is formed as a cylindrical body, and a first outer screw 47A is formed on the outer peripheral portion. The first outer screw 47A is screwed into the female screw 36B2 of the valve accommodating chamber 36B. Thereby, the 1st spring receptacle 47 can move to the direction which can adjust the axial direction dimension of the 1st spring 44, ie, the spring force of the 1st spring 44, by rotating in arbitrary directions. Further, the first spring receiver 47 has a first inner screw 47 </ b> C on an inner peripheral portion sandwiching a contact surface 47 </ b> B with the first spring 44. A second outer screw 48A of the second spring receiver 48 is screwed into the first inner screw 47C.

  The second spring receiver 48 contacts the other side of the second spring 46 and adjusts the urging force of the second spring 46. The second spring receiver 48 is disposed on the inner peripheral side of the first spring receiver 47 so as to face the second valve body 45, and sandwiches the second spring 46 between the second valve body 45. The second spring receiver 48 is formed as a stepped cylindrical body, and a second outer screw 48A is formed on the outer peripheral portion. The second outer screw 48 </ b> A is screwed to the first inner screw 47 </ b> C of the first spring receiver 47. Thus, the second spring receiver 48 can move in a direction in which the axial dimension of the second spring 46, that is, the spring force of the second spring 46 can be adjusted, by rotating in an arbitrary direction.

  The second spring receiver 48 has a contact surface 48B on the second valve body 45 side, and projects from the inner peripheral side of the contact surface 48B toward the second valve body 45 to form a protruding cylinder 48C. . The projecting cylinder 48C has an outflow path 48D through which the working fluid flows out in the axial direction. Here, the protruding cylinder 48 </ b> C serves as a stopper that holds the second spring 46 from the inner peripheral side and restricts the amount of movement of the second valve body 45.

  The reduction side valve mechanism 40 is configured as described above. Next, refer to FIG. 7 for an example of a procedure for assembling the reduction side valve mechanism 40 in the valve accommodating chamber 36B of the reduction side flow path 36. However, it will be explained. The procedure for assembling the expansion side valve mechanism 49 in the valve accommodating chamber 37B of the expansion side flow path 37 is the procedure for assembling the reduction side valve mechanism 40 in the valve accommodating chamber 36B of the reduction side flow path 36. It is omitted because it is the same as.

  The first valve body 42 and the first spring 44 are sequentially inserted into the valve accommodating chamber 36B of the reduction-side flow path 36 from the outside in the radial direction, and the first outer screw 47A of the first spring receiver 47 is inserted into the valve accommodating chamber 36B. Screwed into the female screw 36B2. At this time, the spring force of the first spring 44 can be adjusted to an appropriate value by managing the screwing position (tightening dimension) of the first spring receiver 47, the torque at the time of tightening, and the like.

  After the first valve body 42, the first spring 44, and the first spring receiver 47 are assembled in the valve storage chamber 36B, the second valve body 45, the second spring 46, and the second spring receiver 48 are assembled. In this case, the second valve body 45 and the second spring 46 are disposed in the first spring 44 through the first spring receiver 47, and the guide shaft portion 45 </ b> D of the second valve body 45 is the valve of the first valve body 42. The second spring 46 is brought into contact with the spring contact portion 45B of the second valve body 45 through the passage 42C. Next, the second outer screw 48 </ b> A of the second spring receiver 48 is screwed into the first inner screw 47 </ b> C of the first spring receiver 47 while the protruding cylinder 48 </ b> C is inserted into the second spring 46. At this time, similarly to the first spring receiver 47 described above, by controlling the screwing position (tightening dimension) of the second spring receiver 48, the torque at the time of tightening, etc., the spring force of the second spring 46 is appropriately adjusted. Can be adjusted to the value.

  The hydraulic shock absorber 31 according to the present embodiment has the above-described configuration, and the operation thereof will be described next. The operation of the hydraulic shock absorber 31 is the same in the reduction stroke and the extension stroke, and only the reduction stroke will be described.

  As for the hydraulic shock absorber 31, the cylinder 32 located in the one side is attached to one of a pair of adjacent pillars among the several pillars which support a building, for example. A piston rod 38 is attached to the other column. Thereby, the piston rod 38 can be buffered so as to attenuate the vibration of the building by extending in the axial direction from the cylinder 32 or contracting in the axial direction into the cylinder 32.

  When the piston 35 is displaced in the axial direction at a low speed during the reduction stroke of the piston rod 38, the pressure difference between the one-side oil chamber D and the other-side oil chamber E is small. The flow rate of the hydraulic fluid flowing into the side oil chamber E is also small. For this reason, in the reduction side valve mechanism 40, the second valve body 45 opens against the second spring 46 having a small spring force. Thereby, the second valve body 45 urged in the closing direction by the second spring 46 can impart a damping force to the hydraulic fluid flowing from the one-side oil chamber D toward the other-side oil chamber E, The piston rod 38 can be buffered so as to suppress the reduction operation. The relationship between the displacement speed V of the piston 35 and the damping force F at this time is as shown by a straight line 50 in FIG.

  Further, when the piston 35 is displaced in the axial direction at a high speed during the reduction stroke of the piston rod 38, the pressure difference between the one-side oil chamber D and the other-side oil chamber E becomes large. The flow rate of the hydraulic fluid flowing from D to the other side oil chamber E also increases. For this reason, in the reduction side valve mechanism 40, in addition to the second valve body 45, the first valve body 42 opens against the first spring 44 having a large spring force. Thereby, a damping force can be applied to the hydraulic fluid flowing from the one-side oil chamber D toward the other-side oil chamber E by the first valve body 42 and the second valve body 45, and the reduction operation of the piston rod 38 is suppressed. Can be buffered.

  Here, when the displacement speed V of the piston 35 is fast and a large amount of hydraulic fluid flows from the one-side oil chamber D to the other-side oil chamber E, resistance is generated in the flow channel if the flow channel through which the hydraulic fluid flows is narrow. Therefore, the damping force F is not stable as shown by the curve 51 in FIG.

  However, according to the present embodiment, when the piston rod 38 moves into the reduction-side flow path 36 of the piston 35, the hydraulic fluid flows into the reduction-side flow path 36 toward the radially inner side of the reduction-side flow path 36. A step portion 36B1 of the valve accommodating chamber 36B to be formed is provided. In addition, the reduction-side valve mechanism 40 provided in the reduction-side flow path 36 is inserted into the first valve seat 41 provided in the step portion 36B1 and the reduction-side flow path 36, and one side is separated from the first valve seat 41. A first valve body 42 provided with a valve passage 42C that comes into contact with each other and extends in the separation direction, and one end abuts against the other side of the first valve body 42, and the first valve body 42 is connected to the first valve seat 41. A first spring 44 that is urged in a direction to be seated on the second valve body 45, a second valve body 45 that is in contact with the first valve body 42 from the other side of the first valve body 42, and that can open and close the valve passage 42C. One end of the second valve body 45 is in contact with the other side of the second valve body 45, and the second spring 46 is urged in the direction in which the second valve body 45 is brought into contact with the first valve body 42. The first spring receiver 47 that is in contact with the first spring 44 and is movable in the direction of adjusting the urging force of the first spring 44 and the other side of the second spring 46, and adjusts the urging force of the second spring 46. A second spring bearing 48 is movable in the direction of, and a. In addition, the extension side flow path 37 and the extension side valve mechanism 49 have the same configuration.

  Therefore, the reduction-side valve mechanism 40 includes a high-speed and large-flow first valve body 42 that opens when the displacement speed of the piston 35 is high and a large amount of hydraulic oil flows at a stroke, and a small displacement of the hydraulic oil. The second valve body 45 having a low speed and a small flow rate that is opened when it is distributed can be provided. Thereby, compared with the case where the first valve body 42 having a high speed and a large flow rate and the second valve body 45 having a low speed and a small flow rate are separately provided, a large number (for example, four) of the reduction side valve mechanisms 40 are provided on the piston 35. Therefore, the passage area of the hydraulic fluid can be enlarged. The same applies to the extension side valve mechanism 49.

  As a result, as shown by the straight line 52 in FIG. 8, even when the displacement speed of the piston 35 increases to the maximum speed (Vmax), the damping force can be stably increased to the maximum value (Fmax). Moreover, since the space for installing each valve mechanism 40 and 49 can be made small, the whole hydraulic shock absorber 31 can be reduced in size.

  The first spring receiver 47 is provided with a first outer screw 47 </ b> A that is screwed into a female screw 36 </ b> B <b> 2 provided on the inner peripheral portion of the valve accommodating chamber 36 </ b> B of the reduction side flow path 36 on the outer peripheral portion that forms a cylindrical body. A first inner screw 47C is provided on the inner periphery. On the other hand, the second spring receiver 48 is provided with a second outer screw 48A that is screwed to the first inner screw 47C on the outer periphery. Thus, by managing the screwing positions (tightening dimensions) of the first spring receiver 47 and the second spring receiver 48, the torque at the time of tightening, etc., the spring force of the first spring 44 and the second spring 46 is set to an appropriate value. Can be adjusted. Further, the same effect can be obtained for the extension side valve mechanism 49.

  Next, FIG. 9 shows a third embodiment of the present invention. The feature of this embodiment is that the first spring receiver and the second spring receiver are movably attached to the flow path. Note that in the third embodiment, the same components as those in the first embodiment described above are denoted by the same reference numerals, and description thereof is omitted.

  9, the valve mechanism 61 according to the third embodiment includes a first valve seat 13, a first valve body 14, a second valve seat 15, a second valve body 17, a first spring 62, and a second spring, which will be described later. 63, a first spring receiver 64, and a second spring receiver 65.

  The first spring 62 as the first urging member according to the third embodiment is formed as a compression coil spring, for example, similarly to the first spring 16 according to the first embodiment. However, the first spring 62 according to the third embodiment is set so that the spring length (free length) is shorter than the first spring 16 according to the first embodiment in accordance with the mounting position of the first spring receiver 64 described later. It is different in that it is.

  Similar to the second spring 18 according to the first embodiment, the second spring 63 as the second biasing member according to the third embodiment is formed as a compression coil spring, for example. However, the second spring 63 according to the third embodiment has a spring length (free length) set longer than that of the second spring 18 according to the first embodiment in accordance with the mounting position of the second spring receiver 65 described later. It is different in that it is.

  The first spring receiver 64 according to the third embodiment is formed as a cylindrical body, and the first outer screw 64A on the outer peripheral portion is screwed into the female screw 11B2 of the valve accommodating chamber 11B. The first spring receiver 64 is disposed closer to each valve body 14 and 17 than a second spring receiver 65 described later. The first spring receiver 64 has a contact surface 64 </ b> B in contact with the other end of the first spring 16. Thereby, the 1st spring receiver 64 can move to the direction which can adjust the spring force of the 1st spring 16 by rotating in arbitrary directions.

  The second spring receiver 65 according to the third embodiment is disposed at a position farther from the valve bodies 14 and 17 than the first spring receiver 64. The second spring receiver 65 is formed as a cylindrical body, and a second outer screw 65A on the outer peripheral portion is screwed into the female screw 11B2 of the valve accommodating chamber 11B. The diameter of the second spring receiver 65 is smaller than that of the first spring receiver 64, and the inner peripheral contact surface 65 </ b> B is in contact with the other end of the second spring 18. Thereby, the 2nd spring receiver 65 can move to the direction which can adjust the spring force of the 2nd spring 18 by rotating in arbitrary directions.

  Thus, also in the third embodiment configured as described above, it is possible to obtain substantially the same operational effects as those of the first embodiment described above. In particular, according to the third embodiment, the spring force of the first spring 62 and the spring force of the second spring 63 can be adjusted independently.

  In the first embodiment, the case where the suction valve 7A is provided as the bottom valve of the bottom valve 7 is illustrated. Moreover, the case where check valve 8A is provided as a piston side valve of piston 8 is illustrated. However, the present invention is not limited to this. For example, a valve that generates a damping force may be used as the bottom side valve and the piston side valve.

  In the first embodiment, the second valve body 17 is formed as a stepped cylinder having a large diameter on the distal end side and a small diameter on the proximal end side, and the distal end side is a flat contact surface 17A. Explained with an example. However, the present invention is not limited to this. For example, the second valve body may be formed in a conical shape (conical valve) by reducing the diameter of the distal end side like the first valve body 14. Moreover, you may form the front end surface of a 2nd valve body as a perfect flat surface (plate valve) by abbreviate | omitting guide shaft part 17D. These configurations can be similarly applied to other embodiments.

  In the first embodiment, the case where one valve mechanism 12 is provided in the rod guide 10 has been described as an example. However, the present invention is not limited to this, and a plurality of valve mechanisms 12 may be provided in the rod guide 10.

  In 1st Embodiment, it is set as the structure which adjusts the spring force of the 1st spring 16 by screwing the 1st spring receiver 19 in the valve storage chamber 11B of the flow path 11. As shown in FIG. However, the present invention is not limited to this, and as a means for adjusting the spring force of the first spring 16, a plurality of types of first spring receivers having different dimensions may be prepared and selectively attached. Moreover, you may adjust the spring force of the 1st spring 16 using a spacer. These configurations can be similarly applied to the adjustment of the second spring 18, the springs 44 and 46 according to the second embodiment, and the springs 62 and 63 according to the third embodiment.

  In the second embodiment, the case where four reduction side valve mechanisms 40 and four extension side valve mechanisms 49 are alternately provided on the piston 35 has been described as an example. However, the present invention is not limited to this, and one to three or five or more valve mechanisms 40 and 49 may be provided. Further, the reduction side valve mechanism 40 or the extension side valve mechanism 49 may be arranged adjacent to each other.

  In the second embodiment, the one-side rod guide 33 and the other-side rod guide 34 are provided in the cylinder 32, and the one-side rod guide 33 and the other-side rod guide 34 support the piston rod 38 in a both-end supported state. An example of a configuration is illustrated. However, the present invention is not limited to this, and as in the first embodiment, one rod guide may be a bottom cap and the other rod guide may support the piston rod in a cantilever state.

  Furthermore, in the first embodiment, the case where the hydraulic shock absorber 1 is provided in a railway vehicle is taken as an example, and in the second embodiment, the case where the hydraulic shock absorber 31 is provided in a building is taken as an example. . However, the present invention is not limited to this. For example, various shock absorbers for buffering an object to be buffered, such as a shock absorber for four-wheeled vehicles and two-wheeled vehicles, and a shock absorber for various mechanical devices including general industrial equipment. (Cylinder device) can also be applied.

  As the cylinder device based on the embodiment described above, for example, the following modes can be considered.

  As a first aspect of the cylinder device, a cylinder in which a working fluid is sealed, a partition member that is fitted in the cylinder and partitions the inside of the cylinder into at least two chambers, and a tip extends outside the cylinder. A cylinder having a piston rod that is provided, a flow path that is provided in the partition member and that allows the working fluid to flow between the two chambers, and a valve mechanism that is provided in the flow path and generates a damping force. In the apparatus, the flow path is provided with a step portion formed toward a radially inner side of the flow path on a side into which the working fluid flows when the piston rod moves. Is provided with a first valve seat provided in the stepped portion, a valve passage which is inserted into the flow path, is in contact with the first valve seat in a detachable manner, and extends in the detaching direction. One end abuts against the valve body and the other side of the first valve body. A first urging member that urges the first valve body in a direction to be seated on the first valve seat, and one side from the other side of the first valve body abuts on the first valve body to open and close the valve passage A second valve body provided as possible, and a second urging member that urges the second valve body in a direction in which one end abuts on the other side of the second valve body and abuts the second valve body on the first valve body. A first spring receiver that is in contact with the other side of the first urging member and is movable in a direction in which the urging force of the first urging member is adjusted, and is in contact with the other side of the second urging member. And a second spring receiver that is movable in a direction for adjusting the biasing force of the second biasing member.

  As a second aspect, the first spring receiver is provided with a first outer screw that engages with a screw provided on an inner peripheral portion of the flow path on an outer peripheral portion that forms a cylindrical body, A first inner screw is provided in the portion, and a second outer screw is provided on the outer peripheral portion of the second spring receiver to be engaged with the first inner screw.

1,31 Hydraulic shock absorber (cylinder device)
6 Inner cylinder (cylinder)
8,35 Piston (partition member)
9,38 Piston rod 10 Rod guide (partition member)
11 flow path 11B, 36B, 37B valve accommodating chamber 11B1, 36B1, 37B1 stepped portion 11B2, 36B2, 37B2 female screw 12, 61 valve mechanism 13, 41 first valve seat 14, 42 first valve body 14A, 42A front end surface 14C , 42C Valve passage 15, 43 Second valve seat 16, 44, 62 First spring (first biasing member)
17, 45 Second valve body 18, 46, 63 Second spring (second biasing member)
19, 47, 64 First spring receiver 19A, 47A, 64A First outer screw 19C, 47C First inner screw 20, 48, 65 Second spring receiver 20A, 48A, 65A Second outer screw 32 Cylinder 36 Reduction side flow path (Flow path)
37 Elongation side channel (channel)
40 Reduction side valve mechanism (valve mechanism)
49 Extension side valve mechanism (valve mechanism)
A Reservoir chamber B Rod side oil chamber C Bottom side oil chamber D One side oil chamber E Other side oil chamber

Claims (2)

A cylinder containing a working fluid;
A partition member fitted in the cylinder and partitioning the cylinder into at least two chambers;
A piston rod whose tip extends to the outside of the cylinder;
A flow path that is provided in the partition member and allows the working fluid to flow between the two chambers;
A cylinder device provided in the flow path and generating a damping force,
When the piston rod moves, the flow path is provided with a step formed on the side into which the working fluid flows inward in the radial direction of the flow path.
The valve mechanism is
A first valve seat provided in the step;
A first valve body that is inserted into the flow path, one side of which is detachably contacted with the first valve seat, and provided with a valve passage extending in the separation direction;
A first urging member that urges in a direction in which one end abuts on the other side of the first valve body and seats the first valve body on the first valve seat;
A second valve body provided such that one side from the other side of the first valve body abuts on the first valve body, and the valve passage can be opened and closed;
A second urging member that urges in a direction in which one end abuts on the other side of the second valve body and the second valve body abuts on the first valve body;
A first spring receiver that contacts the other side of the first biasing member and is movable in a direction to adjust the biasing force of the first biasing member;
A second spring receiver that contacts the other side of the second urging member and is movable in a direction to adjust the urging force of the second urging member;
A cylinder device comprising: The first spring receiver is provided with a first outer screw that engages with a screw provided on an inner peripheral portion of the flow path at an outer peripheral portion that forms a cylindrical body, and a first inner screw is provided on the inner peripheral portion. Provided,
2. The cylinder device according to claim 1, wherein the second spring receiver is provided with a second outer screw threadedly engaged with the first inner screw at an outer peripheral portion thereof.

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