JP2013213588A - Damping force adjustment type shock absorber - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain appropriate damping force even during a failure by a simple structure in a damping force adjustment type shock absorber including a pilot-type main valve.SOLUTION: A damping force is generated by controlling an oily fluid flow generated by the slide of a piston within a cylinder 2 by using a pilot-type main valve 27 and a pilot valve 28 as a pressure control valve. The pilot valve 28 adjusts the valve-opening pressure thereof by the thrust of a solenoid actuator S, and also controls the valve-opening pressure of the main valve 27 by adjusting the internal pressure of a pilot chamber 51. When there is a failure, a valve element 58 of the pilot valve 28 is retracted to abut against a fail disk 70 by the spring force of a valve spring 67. Thereby, the damping force is generated by the fail disk 70 on the downstream side of the pilot valve 28, and the appropriate damping force is obtained by controlling the valve-opening pressure of the main valve 27.

Description

    The present invention relates to a damping force adjusting type shock absorber capable of adjusting a damping force.

  A shock absorber mounted on a suspension device of a vehicle such as an automobile has a damping force adjustment type buffer that can appropriately adjust the damping force in order to improve riding comfort and handling stability according to road surface conditions, driving conditions, etc. There is a vessel.

  In general, a damping force adjusting type shock absorber has a piston in which a piston rod is connected in a cylinder in which a fluid is sealed so as to be slidable. The damping force adjustment mechanism is provided. The damping force adjusting mechanism of Patent Document 1 generates a damping force by controlling the flow of fluid by a pilot type damping valve, and further includes a control valve driven by an actuator in a passage for discharging the pilot pressure. The damping force is controlled by controlling the valve.

JP 2001-12534 A

  However, the one described in Patent Document 1 has a problem that the damping force becomes too high because the control valve is closed in a non-energized state such as during a failure.

  An object of the present invention is to provide a damping force adjusting type shock absorber that can obtain an appropriate damping force even in a non-energized state with a simple structure.

  In order to solve the above-described problems, the present invention provides a cylinder in which a fluid is sealed, a piston slidably fitted in the cylinder, and is connected to the piston and extends to the outside of the cylinder. A piston rod, a main valve that generates a damping force by controlling a flow of fluid generated by sliding of the piston in the cylinder, a pilot chamber that applies an internal pressure to the main valve in a valve closing direction, In a damping force adjusting type shock absorber comprising an introduction passage for introducing fluid into a pilot chamber, a pilot passage communicating the pilot chamber and the downstream side of the main valve, and a control valve provided in the pilot passage, The control valve has a valve body that is biased in the valve opening direction by the biasing means, and an actuator that moves the valve body in the valve closing direction by the thrust of a solenoid, A fail valve is provided downstream of the control valve in the pilot passage, and the fail valve is moved when the valve body is urged by the urging means and moves in the valve opening direction of the control valve. And the pilot passage is closed, and when the pressure in the pilot chamber reaches a predetermined pressure, the pilot passage is opened apart from the valve body.

  According to the damping force adjustment type shock absorber according to the present invention, an appropriate damping force can be obtained even in a non-energized state such as during a failure.

It is a longitudinal cross-sectional view which expands and shows the damping force generation mechanism which is the principal part of the damping force adjustment type buffer which concerns on 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the damping force adjustment type shock absorber according to the first embodiment of the present invention. It is a longitudinal cross-sectional view which expands and shows the damping force generation mechanism which is the principal part of the damping force adjustment type buffer which concerns on 2nd Embodiment of this invention. It is a longitudinal cross-sectional view which expands and shows the damping force generation mechanism which is the principal part of the damping force adjustment type buffer which concerns on 3rd Embodiment of this invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
A first embodiment of the present invention will be described with reference to FIGS. 1 and 2.
As shown in FIG. 2, the damping force adjustment type shock absorber 1 according to the present embodiment has a multi-cylinder structure in which an outer cylinder 3 is provided on the outer side of a cylinder 2, and between the cylinder 2 and the outer cylinder 3. A reservoir 4 is formed. A piston 5 is slidably fitted in the cylinder 2, and the inside of the cylinder 2 is defined by the piston 5 as two chambers, a cylinder upper chamber 2A and a cylinder lower chamber 2B. One end of a piston rod 6 is connected to the piston 5 by a nut 7, and the other end side of the piston rod 6 passes through the cylinder upper chamber 2 </ b> A and is a rod guide attached to the upper ends of the cylinder 2 and the outer cylinder 3. 8 and an oil seal 9 are extended to the outside of the cylinder 2. A base valve 10 that partitions the cylinder lower chamber 2 </ b> B and the reservoir 4 is provided at the lower end of the cylinder 2.

  The piston 5 is provided with passages 11 and 12 for communicating between the cylinder upper and lower chambers 2A and 2B. The passage 12 is provided with a check valve 13 that allows only fluid to flow from the cylinder lower chamber 2B side to the cylinder upper chamber 2A side, and the passage 11 contains fluid of the cylinder upper chamber 2A side. A disk valve 14 is provided that opens when the pressure reaches a predetermined pressure and relieves it to the cylinder lower chamber 2B side.

  The base valve 10 is provided with passages 15 and 16 that allow the cylinder lower chamber 2B and the reservoir 4 to communicate with each other. The passage 15 is provided with a check valve 17 that allows only fluid to flow from the reservoir 4 side to the cylinder lower chamber 2B side. In the passage 16, the pressure of the fluid on the cylinder lower chamber 2B side is provided. A disk valve 18 is provided that opens when a predetermined pressure is reached and relieves it to the reservoir 4 side. As the working fluid, an oil liquid is sealed in the cylinder 2, and an oil liquid and a gas are sealed in the reservoir 4.

  A separator tube 20 is externally fitted to the cylinder 2 via seal members 19 at both upper and lower ends, and an annular passage 21 is formed between the cylinder 2 and the separator tube 20. The annular passage 21 is communicated with the cylinder upper chamber 2 </ b> A by a passage 22 provided in a side wall near the upper end portion of the cylinder 2. A small-diameter opening 23 projects from the lower portion of the side wall of the separator tube 20. A large-diameter opening 24 is provided on the side wall of the outer cylinder 3 substantially concentrically with the opening 23, and a damping force generating mechanism 25 is attached to the opening 24 on the side wall of the outer cylinder 3.

Next, the damping force generation mechanism 25 will be described mainly with reference to FIG.
As shown in FIG. 1, the damping force generating mechanism 25 applies a pilot type (back pressure type) main valve 27 and a valve opening pressure of the main valve 27 in a cylindrical case 26 attached to the opening 24 of the outer cylinder. A pilot valve 28 that is a solenoid-driven pressure control valve to be controlled is provided, and a fail valve 29 that operates at the time of failure is provided downstream of the pilot valve 28.

  In the case 26, an annular passage plate 30, a convex passage member 31, an annular main valve member 32, a convex orifice passage member 33, and a cylindrical pilot having a bottom portion in the middle in order from the opening 24 side. A valve member 34, an annular holding member 35, and a cylindrical solenoid case 36 are inserted. These abut against each other and are fixed by connecting the solenoid case 36 to the case 26 with a nut 37.

  The passage plate 30 is fixed in contact with an inner flange 26 </ b> A formed at the end of the case 26. A plurality of passages 38 communicating with the reservoir 4 and the chamber 26B in the case 26 are penetrated through the passage plate 30 along the axial direction. The passage member 31 has a small-diameter leading end that passes through the passage plate 30 and a large-diameter shoulder that abuts against the passage plate 30 and is fixed. The distal end of the passage member 31 is fluid-tightly fitted to the opening 23 of the separator tube 20 via a seal member 39, and a passage 40 passing through the passage member 31 in the axial direction communicates with the annular passage 21. An annular groove 41 is formed at the end of the large-diameter portion of the passage member 31, and the annular groove 41 communicates with the passage 40 through a radial notch 42.

  One end of the main valve member 32 is fixed in contact with the large diameter portion of the passage member 31, and the contact portion between the main valve member 32 and the passage member 31 is sealed by a seal member 43 provided in the annular groove 41. Has been. The main valve member 32 is provided with a plurality of passages 44 extending in the axial direction along the circumferential direction, and the passages 44 communicate with the annular groove 41 of the passage member 31. At the other end of the main valve member 32, an annular seat portion 45 projects from the outer peripheral side of the openings of the plurality of passages 44, and an annular clamp portion 46 projects from the inner peripheral side.

  An outer peripheral portion of a disc valve 47 constituting the main valve 27 is seated on the seat portion 45 of the main valve member 32. The inner peripheral portion of the disc valve 47 is clamped by the clamp portion 46 and the shoulder portion of the large diameter portion of the orifice passage member 33. An annular sliding seal member 48 is fixed to the outer peripheral portion on the back side of the disk valve 47. The convex orifice passage member 33 has a small-diameter portion inserted into the central opening of the main valve member 32, and a shoulder portion having a large-diameter portion is in contact with and fixed to the disc valve 47. A passage 49 passes through the orifice passage member 33 along the axial direction, and the passage 49 communicates with the passage 40 of the passage member 31 via a fixed orifice 50 formed at the tip of the small diameter portion.

  The pilot valve member 34 has a substantially cylindrical shape having a bottom portion 34 </ b> A at an intermediate portion, and one end portion of the bottom portion 34 </ b> A is in contact with and fixed to the orifice passage member 33. A sliding seal member 48 of the disc valve 47 is slidably and fluid-tightly fitted to the inner peripheral surface of the cylindrical portion on one end side of the pilot valve member 34, and a pilot chamber 51 is formed on the back of the disc valve 47. ing. The disc valve 47 is opened by receiving the pressure on the passage 44 side, and the passage 44 communicates with the chamber 26B in the case 26 on the downstream side. The internal pressure of the pilot chamber 51 acts on the disc valve 47 in the valve closing direction. A port 52 passes through the center of the bottom portion 34 </ b> A of the pilot valve member 34, and the port 52 communicates with the passage 49 of the orifice passage member 33. The pilot chamber 51 communicates with the passage 49 through a notch 53 formed in a contact portion of the orifice passage member 33 with the bottom 34A of the pilot valve member 34. The notch 53 and the passage 49 The fixed orifice 50 constitutes an introduction passage for introducing the oil into the pilot chamber 51.

  The holding member 35 is fixed so that the annular convex portion 54 formed on the outer peripheral portion on one end side thereof is in contact with and fixed to the end portion of the cylindrical portion on the other end side of the pilot valve member 34. A valve chamber 55 is formed. The pilot valve member 34 and the holding member 35 are positioned in a radial direction by fitting a cylindrical portion of a solenoid case 36 fitted in the case 26 to an outer peripheral portion. The valve chamber 55 communicates with the chamber 26 </ b> B in the case 26 via a notch 56 formed in the annular convex portion 54 of the holding member 35 and a notch 57 formed in the outer peripheral portion of the cylindrical portion of the pilot valve member 34. ing. The port 52, the valve chamber 55, and the notches 56 and 57 constitute a pilot passage that connects the pilot chamber 51 to the chamber 26B on the downstream side of the disk valve 47 (main valve 27). A valve body 58 of a pilot valve 28 that is a pressure control valve that opens and closes the port 52 is provided in the valve chamber 55.

  The solenoid case 36 incorporates a coil 59, cores 60 and 61 inserted into the coil 59, a plunger 62 guided by the cores 60 and 61, and a hollow operating rod 63 connected to the plunger 62. Yes. The solenoid actuator S is constituted by these, and the distal end portion of the operating rod 63 penetrates the holding member 35 and is connected to the valve body 58 in the valve chamber 55. Then, by energizing the coil 59 via the lead wire 64, an axial thrust is generated in the plunger 62 in accordance with the energizing current.

  The valve body 58 has an annular seat portion 65 formed at a tapered tip portion facing the port 52 of the pilot valve member 34, and the seat portion 65 is seated on and seated on a seat surface 66 around the port 52. 52 is opened and closed. The valve body 58 is normally urged by a spring force of a valve spring 67 (compression coil spring) that is an urging means interposed between the valve body 58 and the bottom 34A of the pilot valve member 34. 1 is in the open position in the retracted position shown in FIG. 1, and moves forward against the spring force of the valve spring 67 by the thrust of the plunger 62 by energizing the coil 59, so that the seat portion 65 moves to the seat surface 66. The port 52 is closed and the valve 52 is closed by adjusting the valve opening pressure by the thrust of the plunger 62, that is, the energization current to the coil 59, thereby controlling the internal pressure of the port 52, that is, the pilot chamber 51.

  A hollow actuating rod 63 passes through the valve body 58. When the valve is closed, that is, when the seat portion 65 is seated on the seat surface 66, the passage 63A in the actuating rod 63 is opened into the port 52, By connecting the port 52 and the chamber 61A at the back of the operating rod 63 in the core 61 by the passage 63A, the pressure receiving area of the port 52 part pressure acting on the valve body 58 is reduced, and the valve body against the thrust of the plunger 62 The variable width of the valve opening pressure 58 can be increased.

Next, the fail valve 28 will be described.
An annular seat portion 58 </ b> A protrudes from the outer peripheral portion of the rear end surface of the valve body 58. One or a plurality of stacked annular seat discs 68 abut against the seat portion 58A, and the seat disc 68 abuts a retaining ring 69 attached to the operating rod 63 at an inner peripheral portion and is fixed to the valve body 58. ing. The outer peripheral portion of the annular fail disk 70 is clamped between the end of the cylindrical portion of the pilot valve member 34 and the annular convex portion 54 of the holding member 35, and the valve body 58 is attached to the inner peripheral edge of the fail disc 70. The flow path between the port 52 and the notch 56 is opened and closed in the valve chamber 55 by the outer peripheral edge of the fixed seat disk 68 being seated.

  An orifice 68A (notch) is provided at the outer peripheral edge of the seat disk 68 or the inner peripheral edge of the fail disk 70 so that the port 52 and the notch 56 are always in communication. A stopper 71 that abuts against the seat disk 68 and restricts the retracted position of the valve body 58 protrudes from the holding member 35. In addition, you may provide the stopper which restrict | limits the retreat position of the valve body 58 in another site | part. The retreat position of the valve body 58 may be restricted at a position where the plunger 62 and the core 61 abut.

  When the coil 59 is not energized, the valve body 58 is retracted by the spring force of the valve spring 67 and the seat disk 68 contacts the fail disk 70 as shown in FIG. The flow path between the port 52 and the notch 56 is closed. In this state, when the pressure of the fluid on the port 52 side in the valve chamber 55 rises and reaches a predetermined pressure, the fail disk 70 bends and the retracted position of the valve body 58 is limited by the stopper 71, and then the seat disk The flow path between the port 52 and the notch 56 is opened apart from 68.

  On the other hand, as described above, in the pressure control state by the pilot valve 28 in which the seat portion 65 of the valve body 58 is seated on the seat surface 66 by energization of the coil 59, the seat disc 68 is separated from the fail disc 70, and the valve The flow path between the port 52 and the notch 56 in the chamber 55 is in a communication state through the opening in the center of the fail disk 70.

Next, the operation of the present embodiment configured as described above will be described.
The damping force adjusting type shock absorber 1 is mounted between the sprung springs of the vehicle suspension device, the lead wire 64 is connected to an in-vehicle controller or the like. The seat portion 65 is seated on the seat surface 66 and pressure control by the pilot valve 28 is executed.

  During the extension stroke of the piston rod 6, the check valve 13 of the piston 5 is closed by the movement of the piston 5 in the cylinder 2, and the fluid on the cylinder upper chamber 2A side is pressurized before the disc valve 14 is opened. Then, it passes through the passage 22 and the annular passage 21 and flows into the passage 40 of the passage member 31 of the damping force generation mechanism 25 from the opening 23 of the separator tube 20.

  At this time, the fluid corresponding to the movement of the piston 5 opens the check valve 17 of the base valve 10 from the reservoir 4 and flows into the cylinder lower chamber 2B. When the pressure in the cylinder upper chamber 2A reaches the valve opening pressure of the disk valve 14 of the piston 5, the disk valve 14 is opened, and the pressure in the cylinder upper chamber 2A is relieved to the cylinder lower chamber 2B. Prevent excessive pressure rise of 2A.

  In the damping force generating mechanism 25, the fluid that has flowed in from the passage 40 of the passage member 31 is fixed to the fixed orifice 50 and the passage 49 of the orifice passage member 33 before the disk valve 47 of the main valve 27 is opened (piston speed low speed region). The valve body 58 of the pilot valve 28 is pushed open through the port 52 of the pilot valve member 34 and flows into the valve chamber 55. Further, the gas flows through the opening of the fail disk 70 and flows into the reservoir 4 through the notch 56 of the holding member 35, the notch 57 of the pilot valve member 34, the chamber 26 </ b> B in the case 26 and the passage 38 of the passage plate 30. When the piston speed increases and the pressure on the cylinder upper chamber 2A side reaches the valve opening pressure of the disc valve 47, the fluid flowing into the passage 40 passes through the notch 42, the annular groove 41 and the passage 44, and passes through the disc valve. 47 is pushed open to flow directly into the chamber 26B in the case 26.

  During the contraction stroke of the piston rod 6, the check valve 13 of the piston 5 is opened by the movement of the piston 5 in the cylinder 2, the check valve 17 of the passage 15 of the base valve 10 is closed, and before the disk valve 18 is opened. The fluid in the piston lower chamber 2B flows into the cylinder upper chamber 2A, and the fluid corresponding to the piston rod 6 that has entered the cylinder 2 flows from the cylinder upper chamber 2A through the same path as in the extension stroke to the reservoir. It flows to 4. When the pressure in the cylinder lower chamber 2B reaches the valve opening pressure of the disk valve 18 of the base valve 10, the disk valve 18 is opened, and the pressure in the cylinder lower chamber 2B is relieved to the reservoir 4, thereby Prevent excessive pressure rise of 2B.

  As a result, during the expansion / contraction stroke of the piston rod 6, the damping force generating mechanism 25, before opening the disk valve 47 of the main valve 27 (piston speed low speed region), the fixed orifice 50 and the valve body 58 of the pilot valve 28. A damping force is generated by the valve opening pressure, and after the disk valve 47 is opened (piston speed high speed region), a damping force is generated according to the opening degree. The damping force can be directly controlled regardless of the piston speed by adjusting the valve opening pressure of the pilot valve 28 with the energization current to the coil 59. At this time, the internal pressure of the back pressure chamber 55 communicating with the upstream passage 49 is changed by the valve opening pressure of the pilot valve 28, and the internal pressure of the back pressure chamber 55 acts in the valve closing direction of the disc valve 47. By controlling the valve opening pressure of the pilot valve 28, the valve opening pressure of the disc valve 47 can be adjusted at the same time, and thereby the adjustment range of the damping force characteristic can be widened.

  At this time, if the energization current to the coil 59 is decreased and the thrust of the plunger 62 is decreased, the valve opening pressure of the pilot valve 28 is reduced, a soft-side damping force is generated, and the energization current is increased. When the thrust of the plunger 62 is increased, the valve opening pressure of the pilot valve 28 increases and a hard-side damping force is generated. Therefore, a soft-side damping force that is generally used frequently can be generated at a low current. And power consumption can be reduced.

  When the thrust of the plunger 62 is lost due to the occurrence of a failure such as the disconnection of the coil 59 or the failure of the in-vehicle controller, the valve body 58 is retracted to the position shown in FIG. 52 opens, the seat disk 68 of the valve body 58 contacts the fail disk 70, and the flow path between the port 52 and the notch 56 in the valve chamber 55 is closed. In this state, the flow of fluid from the port 52 to the notch 56 in the valve chamber 55 is controlled by the fail valve 29, that is, the orifice 68A and the fail disk 70. A desired damping force can be generated by setting the valve opening pressure of the fail disk 70, and the internal pressure of the pilot chamber 51, that is, the valve opening pressure of the main valve 27 can be adjusted. As a result, an appropriate damping force can be obtained even during a failure.

  Thus, since the fluid passage at the time of energization and the fluid passage at the time of failure are made common (in series), the structure can be simplified and the space efficiency can be improved. Further, since the fail disc 70 is a disc valve, the passage at the time of fail is opened and closed by the end of the disc valve and the valve body, for example, compared to a configuration using a ball valve, so that productivity and assembly are improved. Can be increased. In addition, since a soft-side damping force that is frequently used is generally obtained by energizing the coil 59 with a low current, the power consumption can be reduced. Therefore, it is possible to secure the steering stability of the vehicle, to realize a fail safe, and to prevent adverse effects such as an increase in vibration input to the vehicle body by fixing on the hardware side. be able to.

  Next, a second embodiment of the present invention will be described with reference to FIG. Note that the same reference numerals are used for the same parts with respect to the first embodiment, and only different parts will be described in detail.

  As shown in FIG. 3, in this embodiment, the outer peripheral portion of the fail disc 70 of the fail valve 29 is not clamped and is inserted into an inner peripheral groove 72 formed by the holding member 35 and the pilot valve member 34. Thus, it is supported in a floating manner so as to be movable by a certain distance in the axial direction. Further, the annular convex portion 67 and the seat disk 68 of the valve body 58 are omitted, and the outer peripheral edge portion of the end face of the valve body 58 is in direct contact with the inner peripheral edge portion of the fail disc 70. The orifice 68A can be provided at the inner peripheral edge of the fail disc 70 or the outer peripheral edge of the end face of the valve body 58. The valve chamber 55 includes a passage 77 passing through the holding member 35 in the axial direction, a notch 78 formed at the end of the holding member, a notch 79 formed at the outer peripheral portion, and a cutout of the pilot valve member 34. It communicates with the chamber 26 </ b> B in the case 26 through the notch 57. Thereby, there can exist an effect similar to the said 1st Embodiment. Furthermore, durability can be improved in the present embodiment.

  Next, a third embodiment of the present invention will be described with reference to FIG. Note that the same reference numerals are used for the same parts with respect to the first embodiment, and only different parts will be described in detail.

  As shown in FIG. 4, in this embodiment, the holding member 35 is omitted, the solenoid case 36 abuts on the end of the cylindrical portion of the pilot valve member 34, and the notch 56 that communicates with the valve chamber 55 has a pilot portion. It is formed at the end of the cylindrical portion of the valve member 34. The fail disk 73 of the fail valve 29 has an inner peripheral portion attached to a cylindrical portion 60 </ b> A protruding from the core 60 so that the outer peripheral portion bends. The cylindrical portion 60A also serves as a stopper for the valve body 58. Further, the valve body 58 of the pilot valve 28 is formed with an enlarged diameter portion 74 at the base end portion, and the outer peripheral portion of the enlarged diameter portion 74 is guided in sliding contact with the inner peripheral surface of the cylindrical portion of the pilot valve member 34. . In the enlarged diameter portion 74, a plurality of passages 75 are penetrated in the axial direction so as to face the fail disc 73, and an annular seat portion 76 on which the fail disc 73 is seated projects from the outer peripheral portion of the plurality of passages 75. . The orifice 68A can be formed in the outer peripheral portion of the fail disk 73 or the sheet portion 76.

  With this configuration, in the valve chamber 55, the fluid flows to the notch 56 through the passage 75 of the enlarged diameter portion 74 of the valve body 58. At the time of failure, as shown in FIG. 4, the seat portion 76 of the enlarged diameter portion 74 of the valve body 58 contacts the fail disk 73 to close the passage 75, and the valve body 58 is retracted by the pressure on the port 52 side. After contacting the cylindrical portion 60 </ b> A as a stopper, the fail disk 73 is bent and separated from the sheet portion 76, thereby opening the passage 75. Thereby, there exists an effect similar to the said 1st Embodiment.

  In the first to third embodiments, the working fluid uses oil and gas for the sake of stability of operation and convenience of handling. However, the present invention is not limited to this, and other fluids are used alone. Or they can be used in combination. In addition, the cross-sectional shape of the constituent members such as the piston, cylinder, and valve is preferably circular in view of sealing performance, workability, and the like, but may be other shapes such as a polygon.

  Moreover, although the said 1st thru | or 3rd embodiment showed the example which provided the damping-force generation | occurrence | production mechanism 25 on the side of a cylinder, if the flow of an oil liquid arises by sliding of a piston, it will be in a piston part, for example. It may be provided.

  Furthermore, in the first to third embodiments, an example in which the pilot valve 28 is a pressure control valve has been described, but a flow rate control valve for controlling the flow rate may be used.

  In the first to third embodiments, the pilot chamber 51 and the valve chamber 55 are separated from each other, and the notch 53 is connected between them. However, the pilot chamber 51 and the valve chamber 55 are connected to each other. The notch 53 may be eliminated as a common chamber.

  In the first to third embodiments, an example is shown in which one end of the valve body 58 of one lump functions as the valve portion of the control valve and the other end functions as the valve seat of the fail valve. Although it becomes complicated, it is good also as a structure which divides the valve part of a control valve and the valve seat of a fail valve into two bodies, and connects them.

  DESCRIPTION OF SYMBOLS 1 ... Damping force adjustment type buffer, 2 ... Cylinder, 27 ... Main valve, 28 ... Pilot valve (pressure control valve), 29 ... Fail valve, 49 ... Passage (introduction passage), 50 ... Fixed orifice (introduction passage), 53 ... Notch (introduction passage), 52 ... Port (pilot passage), 55 ... Valve chamber (pilot passage), 56, 57 ... Notch (pilot passage), 58 ... Valve body, 67 ... Valve spring (biasing) Means), S ... Solenoid actuator

In order to solve the above-described problems, the present invention provides a cylinder in which a fluid is sealed, a piston slidably fitted in the cylinder, and is connected to the piston and extends to the outside of the cylinder. A piston rod, a main valve that generates a damping force by controlling a flow of fluid generated by sliding of the piston in the cylinder, a pilot chamber that applies an internal pressure to the main valve in a valve closing direction, In a damping force adjusting type shock absorber comprising an introduction passage for introducing fluid into a pilot chamber, a pilot passage communicating the pilot chamber and the downstream side of the main valve, and a control valve provided in the pilot passage, The control valve has a valve body that is biased in the valve opening direction by the biasing means, and an actuator that moves the valve body in the valve closing direction by the thrust of a solenoid, Fail valve is provided downstream of the control valve of the serial pilot passage, the valve body of the control valve is provided in the valve chamber, the valve chamber has one end open to the pilot chamber side, the other end said fail valve One end side of the valve chamber is opened and closed by one end side of the valve body, the other end side is opened and closed by the fail valve and the other end side of the valve body, and the fail valve is When the body is biased by the biasing means and moves in the valve opening direction of the control valve, the pilot passage is closed by contacting the valve body, and when the pressure in the pilot chamber reaches a predetermined pressure, the valve The pilot passage is opened apart from the body.

Claims (7)

A cylinder filled with fluid, a piston slidably fitted in the cylinder, a piston rod connected to the piston and extending to the outside of the cylinder, and sliding of the piston in the cylinder A main valve that generates a damping force by controlling the flow of fluid generated by the pilot, a pilot chamber that applies an internal pressure to the main valve in a valve closing direction, an introduction passage that introduces fluid into the pilot chamber, and the pilot In a damping force adjustment type shock absorber comprising a pilot passage communicating the chamber and the downstream side of the main valve, and a control valve provided in the pilot passage,
The control valve has a valve body that is biased in the valve opening direction by the biasing means, and an actuator that moves the valve body in the valve closing direction by the thrust of a solenoid,
A fail valve is provided downstream of the control valve in the pilot passage;
When the valve body is urged by the urging means and moves in the valve opening direction of the control valve, the fail valve abuts on the valve body to close the pilot passage, and the pressure in the pilot chamber is a predetermined pressure. The damping force adjusting type shock absorber is characterized by opening the pilot passage away from the valve body when reaching the value.   2. The damping force adjusting type shock absorber according to claim 1, wherein an orifice is formed in at least one of the fail valve and the valve body that contacts the fail valve.   3. The damping force adjusting type shock absorber according to claim 1, wherein the control valve is a pressure control valve that opens when the pressure of the pilot passage reaches a predetermined pressure.   The valve body of the control valve is provided in a valve chamber, and the valve chamber has one end opened on the pilot chamber side and the other end opened on the downstream side of the fail valve. 4. A damping force adjusting type shock absorber according to any one of 3 above.   The one end side of the valve chamber is opened and closed by one end side of the valve body, and the other end side is opened and closed by the other end side of the fail valve and the valve body. The damping force adjustment type shock absorber described.   The damping force adjusting type shock absorber according to any one of claims 1 to 5, wherein an annular seat portion that contacts the fail valve is provided on the other end side of the valve body.   The damping force adjusting type shock absorber according to any one of claims 1 to 6, wherein the fail valve is a disk valve.

Images