WO2018155293A1 - Shock absorber - Google Patents

Shock absorber Download PDF

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Publication number
WO2018155293A1
WO2018155293A1 PCT/JP2018/005179 JP2018005179W WO2018155293A1 WO 2018155293 A1 WO2018155293 A1 WO 2018155293A1 JP 2018005179 W JP2018005179 W JP 2018005179W WO 2018155293 A1 WO2018155293 A1 WO 2018155293A1
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WO
WIPO (PCT)
Prior art keywords
pressure
extension
valve
chamber
passage
Prior art date
Application number
PCT/JP2018/005179
Other languages
French (fr)
Japanese (ja)
Inventor
瞭太 五味
萩平　慎一
敦 作田
Original Assignee
Ｋｙｂ株式会社
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Filing date
Publication date
Application filed by Ｋｙｂ株式会社 filed Critical Ｋｙｂ株式会社
Publication of WO2018155293A1 publication Critical patent/WO2018155293A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
    • F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping

Definitions

  • This invention relates to a shock absorber.
  • shock absorbers used in vehicle suspensions have a damping valve that can vary the damping force.
  • a shock absorber includes a cylinder, a piston that divides the cylinder into an extension side chamber and a pressure side chamber, a piston rod that is connected to the piston at one end and is movably inserted into the cylinder, and a damping valve. Composed.
  • the damping valve opens and closes an extension side passage and a pressure side passage, which communicate with the extension side chamber and the pressure side chamber provided in the piston, and opens and closes the extension side passage and the pressure side passage, respectively.
  • the expansion side leaf valve, the compression side leaf valve, the expansion side spool and the compression side spool that press the expansion side leaf valve and the compression side leaf valve, respectively, the expansion side back pressure chamber and the compression side back that press the expansion side spool and the compression side spool with internal pressure
  • an electromagnetic pressure control valve for adjusting the pressure in the pressure chamber.
  • the damping force at the time of expansion and contraction can be controlled by controlling the pressure in the expansion-side back pressure chamber and the pressure-side back pressure chamber by a single electromagnetic pressure control valve.
  • the extension side back pressure chamber and the pressure side back pressure chamber are connected by a communication path.
  • the communication passage communicates with the electromagnetic pressure control valve.
  • This communication path is formed by an annular gap formed on the outer periphery of the separator by providing a vertical hole in the holding shaft of the piston holder that holds the piston, and inserting a pipe-shaped separator into the vertical hole.
  • the strength of the piston holder is inevitably lowered due to the fact that a vertical hole is provided in the holding shaft and the separator is inserted.
  • an object of the present invention is to provide a shock absorber capable of reducing the number of parts and ensuring the strength of the piston holder.
  • the expansion-side back pressure chamber that urges the expansion-side spool toward the expansion-side leaf valve and the compression-side back pressure chamber that urges the compression-side spool toward the compression-side leaf valve communicate with each other. Since the communication path is formed on the outer periphery of the holding shaft, there is no need to provide a separator for providing the communication path in the holding shaft.
  • FIG. 1 is a cross-sectional view of a shock absorber according to an embodiment.
  • FIG. 2 is an enlarged cross-sectional view of the electromagnetic pressure control valve of the shock absorber in one embodiment.
  • FIG. 3 is an enlarged cross-sectional view of the piston portion of the shock absorber according to the embodiment.
  • the shock absorber D in one embodiment opens and closes a cylinder 1, an annular piston 2 that is slidably inserted into the cylinder 1, and an extension-side passage 3 provided in the piston 2.
  • An extension side leaf valve Ve a pressure side leaf valve Vp that opens and closes a pressure side passage 4 provided in the piston 2, an extension side chamber member 12 and an extension side spool Se, a pressure side chamber member 11 and a pressure side spool Sp, and a piston holder 8
  • the groove 8h functioning as a communication path, the expansion pilot orifice Pe as the expansion resistance element, the compression pilot orifice Pp as the compression resistance element, the adjustment path Pc connected to the groove 8h, and the adjustment path Pc
  • a pressure side discharge passage Ep that allows only the flow of liquid toward the side chamber R1, and an extension side discharge that allows only the flow of liquid from the adjustment passage Pc to the pressure side chamber R2.
  • road Ee is constituted by an electromagnetic pressure control valve 6 provided in the regulation passage Pc to control the upstream pressure regulating passage Pc.
  • the cylinder 1 is filled with a liquid such as hydraulic oil, the lower end is closed, although not shown, and an annular rod guide is attached to the upper end.
  • a free piston that slides in the cylinder 1 is provided below the cylinder 1 in FIG. 1, and a gas chamber is formed in the cylinder 1 by the free piston.
  • the liquid with which the cylinder 1 is filled can be used if it is a liquid which can exhibit damping force besides hydraulic oil.
  • the piston 2 is slidably inserted into the cylinder 1, and defines an extension side chamber R1 and a pressure side chamber R2 filled with liquid in the cylinder 1, and is movably inserted into the cylinder 1. It is connected to one end of the piston rod 7.
  • the piston rod 7 is inserted through the inner periphery of the rod guide (not shown) provided at the upper end of the cylinder 1 and protrudes outside the cylinder 1.
  • a seal (not shown) is provided between the piston rod 7 and the cylinder 1, and the cylinder 1 is in a liquid-tight state.
  • the shock absorber D Since the shock absorber D is set to a so-called single rod type, the volume of the piston rod 7 that enters and exits the cylinder 1 as the shock absorber D expands and contracts is the volume of the gas in the gas chamber described above. By expanding or contracting, the free piston moves up and down in the cylinder 1 to be compensated. As described above, the shock absorber D is set to a single cylinder type, but instead of installing a free piston and a gas chamber, a reservoir is provided on the outer periphery or outside of the cylinder 1 and the volume compensation of the piston rod 7 is performed by the reservoir. May be performed.
  • the piston rod 7 has a piston holder 8 that holds the piston 2 and an electromagnetic valve housing that forms a hollow housing portion L that is connected to the piston holder 8 and that houses the electromagnetic pressure control valve 6 together with the piston holder 8.
  • a cylinder 9 and a rod member 10 having one end connected to the solenoid valve housing cylinder 9 and the other end protruding outward from the upper end of the cylinder 1 are formed.
  • the piston holder 8 includes a holding shaft 8a on which the annular piston 2 is mounted on the outer periphery, a flange 8b provided on the outer periphery of the upper end of the holding shaft 8a in FIG. 1, and a cylindrical shape provided on the outer periphery of the upper end of the flange 8b in FIG. And a socket 8c.
  • the piston holder 8 is opened from the tip of the holding shaft 8a, extends in the axial direction, communicates with the socket 8c, a port 8e that passes through the flange 8b and communicates with the socket 8c, and a diagram of the holding shaft 8a.
  • the solenoid valve housing cylinder 9 includes a top-cylindrical housing cylinder portion 9a and a cylindrical connecting portion that has an outer diameter smaller than that of the housing cylinder portion 9a and extends upward from the top of the housing cylinder portion 9a in FIG. 9b and a through-hole 9c that opens from the side of the accommodating tube portion 9a and communicates with the inside. Then, when the socket 8c of the piston holder 8 is screwed to the inner periphery of the accommodating cylinder portion 9a of the electromagnetic valve accommodating cylinder 9 and the piston holder 8 is integrated with the electromagnetic valve accommodating cylinder 9, the electromagnetic valve accommodating cylinder 9 and the piston holder are integrated.
  • the accommodating part L in which the electromagnetic pressure control valve 6 is accommodated is formed in the accommodating cylinder part 9a.
  • the accommodating portion L functions as a part of the adjustment passage Pc, communicates with the groove 8h provided on the outer periphery of the holding shaft 8a via the port 8e, and forms the extension-side discharge passage Ee.
  • the pressure side chamber R2 communicates with the vertical hole 8d.
  • the through hole 9c faces the recess 8i, and cooperates with the through hole 8j to allow the housing portion L to communicate with the extension side chamber R1. It is like that.
  • an annular valve body 22a is attached to the recess 8i provided on the outer periphery of the upper end in FIG. 1 of the socket 8c.
  • the annular valve body 22a is urged by a spring 22b from above in FIG. Open and close.
  • the annular valve body 22 a and the spring 22 b constitute a check valve 22.
  • the pressure-side discharge passage Ep is formed by a through-hole 9c, a recess 8i, and a through-hole 8j, and only the flow of liquid from the adjustment passage Pc to the extension-side chamber R1 is allowed by the check valve 22 described above. Block the flow of liquid in the opposite direction.
  • the above-described vertical hole 8d provided in the holding shaft 8a functions as the extension side discharge passage Ee, and the vertical hole 8d provided in the holding shaft 8a goes from the accommodating portion L to the compression side chamber R2 through the vertical hole 8d.
  • a check valve 25 that allows only the flow of liquid is provided.
  • the check valve 25 is seated on the pipe 25a mounted in the vertical hole 8d, a cup-shaped spring receiver 25b fitted to the pipe 25a, and an end of the pipe 25a and accommodated in the spring receiver 25b.
  • a disc-like valve body 25c, and a spring 25d interposed between the top of the spring receiver 25b and the valve body 25c.
  • the spring receiver 25b is provided with a notch, and when the valve body 25c is separated from the pipe 25a, the check valve 25 is opened to allow the flow of liquid from the vertical hole 8d side toward the pressure side chamber R2.
  • the valve body 25c contacts the lower end of the pipe 25a in FIG. 1 and the check valve 25 closes to block the liquid flow.
  • the check valve 25 is assembled and accommodated in the vertical hole 8d, and is fixed to the vertical hole 8d by a disc spring fitted near the outlet of the vertical hole 8d. Therefore, the extension side discharge passage Ee blocks the flow of liquid from the pressure side chamber R2 toward the adjustment passage Pc, and allows only the flow of liquid from the adjustment passage Pc toward the pressure side chamber R2.
  • the rod member 10 has a cylindrical shape, and the inner circumference at the lower end in FIG. 1 has an enlarged diameter, allows insertion of the connecting portion 9b of the solenoid valve housing cylinder 9, and enables the connecting portion 9b to be screwed. A screw portion (not shown) is provided. Thus, when the rod member 10, the solenoid valve housing cylinder 9, and the piston holder 8 are integrated, the piston rod 7 is formed by these.
  • a harness H for supplying power to a solenoid which will be described later, is inserted into the rod member 10 and the connecting portion 9b of the solenoid valve housing cylinder 9, and the upper end of the harness H is not shown, but the upper end of the rod member 10 is not shown. Is connected to the power supply.
  • the outer periphery of the holding shaft 8 a provided in the piston holder 8 slides on the outer periphery of the shim 61 and the shim 61 formed by laminating a plurality of annular plates together with the annular piston 2.
  • a pressure-side annular plate 62 that is freely mounted, a pressure-side stopper 63 that is annular and has an outer diameter larger than that of the shim 61, and the pressure-side chamber member 11 are assembled in an overlapping manner.
  • annular pressure side leaf valve Vp that is slidably mounted on the outer periphery of the shim 61 is provided on the piston 2, and the pressure side leaf valve Vp is connected to the holding shaft of the piston holder 8 via the shim 61. It is attached to the outer periphery of 8a.
  • the pressure side chamber member 11 is slidably mounted with a pressure side spool Sp that is in contact with the pressure side annular plate 62, and the pressure side spool Sp is movable in the axial direction so as to move together with the pressure side chamber member 11. Is forming.
  • a shim 65 as a shaft member configured by laminating a plurality of annular plates, and an extended-side annular plate 66 that is slidably mounted on the outer periphery of the shim 65,
  • An extension side stopper 67 and an extension side chamber member 12 which are annular and have an outer diameter larger than that of the shim 65 are assembled in an overlapping manner.
  • an annular extension side leaf valve Ve that is slidably mounted on the outer periphery of the shim 65 is provided on the piston 2, and the extension side leaf valve Ve is connected to the piston holder 8 via the shim 65. It is attached to the outer periphery of the holding shaft 8a.
  • An extension side spool Se that contacts the extension side annular plate 66 is slidably attached to the extension side chamber member 12, and the extension side spool Se can be moved in the axial direction.
  • an extension side back pressure chamber Ce is formed.
  • the outer diameter of the extension side leaf valve Ve is smaller than the outer diameter of the compression side leaf valve Vp.
  • each component mounted on the outer periphery of the holding shaft 8a described above is fixed by the extension-side chamber member 12 screwed into a screw portion 8f formed at the tip of the holding shaft 8a.
  • the piston 2 is annular and is mounted on the outer periphery of the holding shaft 8a of the piston holder 8, and an extension side passage 3 and a pressure side passage 4 that connect the extension side chamber R1 and the pressure side chamber R2 are formed.
  • 3 at the upper end of the piston 2, there is an annular window 2a communicating with the pressure side passage 4, an annular pressure side valve seat 2b provided on the outer peripheral side of the annular window 2a and surrounding the pressure side passage 4, and an annular window 2a.
  • seat part 2c provided in the inner periphery is provided.
  • annular window 2d communicated with the extension side passage 3
  • annular extension side valve seat 2e provided on the outer peripheral side of the annular window 2d and surrounding the extension side passage 3, and an annular window 2d.
  • seat part 2f provided in the inner periphery is provided.
  • the extension-side leaf valve Ve is annular in order to allow insertion of the holding shaft 8 a of the piston holder 8.
  • the extension-side leaf valve Ve is composed of a single annular plate. It may be configured by laminating a single annular plate.
  • the extension side leaf valve Ve configured as described above is overlapped below the piston 2 in FIG. 3 and can be attached to and detached from the extension side valve seat 2e and the inner peripheral seat portion 2f.
  • the extension side leaf valve Ve is provided with a notch Oe that functions as an orifice when seated on the extension side valve seat 2e on the outer periphery thereof, and is slidably mounted on the outer periphery of the shim 65.
  • an expansion side annular plate 66 that is superimposed on the expansion side leaf valve Ve is slidably mounted.
  • an annular auxiliary valve 71 having an outer diameter smaller than that of the expansion side annular plate 66 is stacked on the side of the expansion side annular plate 66 opposite to the leaf valve side.
  • the outer periphery of the shim 65 is slidably mounted.
  • the axial length when the extension-side leaf valve Ve, the extension-side annular plate 66 and the auxiliary valve 71 are stacked is made shorter than the axial length of the shim 65.
  • an extension side stopper 67 is provided below the shim 65 in FIG. 3 and has an annular shape whose outer diameter is set larger than the inner diameters of the auxiliary valve 71 and the extension side annular plate 66.
  • the extension side chamber member 12 is stacked below the side stopper 67. Accordingly, the extension side leaf valve Ve, the extension side annular plate 66 and the auxiliary valve 71 are guided by the shim 65 so as to be movable in the vertical direction in FIG. 3 which is the axial direction between the piston 2 and the extension side stopper 67. It has become.
  • the extension-side leaf valve Ve When the extension-side leaf valve Ve is pressed by pressure from the extension-side passage 3 side, the outer periphery bends together with the extension-side annular plate 66, and the extension-side leaf plate Ve and the auxiliary valve 71 as a whole are separated from the piston 2. Can retreat.
  • the retraction amounts of the extension side leaf valve Ve, the extension side annular plate 66 and the auxiliary valve 71 from the piston 2 are set by the axial length of the shim 65.
  • the shim 65 is constituted by a plurality of annular plates, the shim 65 can be adjusted by the number of laminated annular plates, but the shim 65 may be constituted by a single annular plate.
  • the expansion side annular plate 66 is bent and has higher rigidity than the expansion side leaf valve Ve. For this reason, the axial length (thickness) of the expansion side annular plate 66 is longer than the axial length (thickness) of the expansion side leaf valve Ve.
  • the expansion-side annular plate 66 may be formed of a material having higher rigidity than the side leaf valve Ve.
  • the inner diameter of the expansion side annular plate 66 is set to be smaller than the outer diameter of the inner peripheral sheet portion 2f provided in the piston 2.
  • the outer diameter of the expansion side annular plate 66 is set to be larger than the inner diameter of the expansion side valve seat 2e.
  • the extension-side back pressure chamber Ce urges the extension-side spool Se toward the extension-side annular plate 66 with the pressure introduced inside. Therefore, the extension side leaf valve Ve stacked on the extension side annular plate 66 is urged toward the piston 2 by the urging force received from the extension side spool Se and the pressure of the extension side back pressure chamber Ce.
  • the extension side annular plate 66 When the expansion side annular plate 66 is pressed from the back side by the pressure in the expansion side back pressure chamber Ce and the expansion side spool Se, and the expansion side leaf valve Ve is seated on the expansion side valve seat 2e and the inner peripheral seat portion 2f, The extension side annular plate 66 is supported by the inner peripheral seat portion 2f and the extension side valve seat 2e. Therefore, the pressure in the extension side back pressure chamber Ce and the urging force of the extension side spool Se are received by the extension side annular plate 66, and deformation of the extension side leaf valve Ve is suppressed, and the extension side leaf valve Ve is overloaded. It is not to take.
  • the auxiliary valve 71 has an outer diameter smaller than that of the extension side leaf valve Ve and the extension side annular plate 66.
  • auxiliary valve 71 when the extension side leaf valve Ve and the extension side annular plate 66 are bent by the pressure of the extension side passage 3, the outer peripheral side is more easily bent than the auxiliary valve 71.
  • the damping characteristic of damping force can be tuned. If the auxiliary valve 71 is unnecessary due to the damping characteristic generated in the shock absorber D, it can be omitted. Conversely, a plurality of auxiliary valves 71 may be stacked.
  • the extension-side chamber member 12 is disposed on the opposite side of the extension-side leaf valve Ve from the piston, and has a cylindrical spacer 121 that is screwed to the outer periphery of the holding shaft 8a of the piston holder 8, and an outer periphery of the spacer 121. And a sliding contact cylinder 122 that is fitted and in sliding contact with the expansion side spool Se.
  • the spacer 121 includes a cylindrical portion 121a that is screwed to the screw portion 8f of the holding shaft 8a, a flange 121b that is provided on the outer periphery of the lower end in FIG.
  • the sliding contact cylinder 122 includes a cylindrical portion 122a in which the extension side spool Se is in sliding contact with the inner periphery, and a flange 122b that protrudes to the inner periphery at the lower end in FIG. 3 of the cylindrical portion 122a.
  • the cylindrical portion 121a of the spacer 121 is fitted to the inner periphery of the flange 122b of the sliding contact tube 122.
  • the spacer 121 and the sliding contact tube 122 are integrated to form an annular recess.
  • the extension-side back pressure chamber Ce is formed by the annular recess.
  • the extension side chamber member 12 is constituted by the spacer 121 and the sliding contact cylinder 122 in order to facilitate processing, but may be constituted by one part.
  • the annular groove 121c on the inner periphery of the spacer 121 faces the groove 8h provided on the holding shaft 8a, and the extension side back pressure chamber Ce passes through the pressure side pilot orifice Pp. It communicates with the groove 8h.
  • An extension side stopper 67 is interposed between the spacer 121 and the shim 65 in the extension side chamber member 12, but the extension side stopper 67 is abolished so that the spacer 121 functions as a stopper.
  • the lower limit of movement of the plate 66 may be restricted.
  • the extension side spool Se is accommodated in the sliding tube 122.
  • the extension-side spool Se is in sliding contact with the inner periphery of the cylindrical portion 122 a of the sliding contact cylinder 122, and can move in the axial direction within the sliding contact cylinder 122.
  • the extension-side spool Se includes an annular spool body 13 and an annular protrusion 14 that rises from the inner periphery of the upper end of the spool body 13 in FIG.
  • the inner diameter of the annular protrusion 14 is set to be smaller than the outer diameter of the extended-side annular plate 66 so that the annular protrusion 14 can come into contact with the lower surface in FIG. Yes.
  • the inner diameter of the spool body 13 is larger than the outer diameter of the cylindrical portion 121a of the spacer 121, but the inner diameter is set to a diameter that is in sliding contact with the outer periphery of the cylindrical portion 121a to extend the extension-side back pressure chamber Ce. You may seal with the side spool Se.
  • the sliding contact cylinder 122 of the extension side chamber member 12 is provided with a pressure side pressure introduction passage Ip that passes through the flange 122b and communicates the extension side back pressure chamber Ce and the pressure side chamber R2.
  • An annular valve body 15 is superimposed on the upper end of the flange 122b of the sliding contact cylinder 122 in FIG. 3, and is annularly formed by a spring 16 interposed between the annular valve body 15 and the spool body 13 of the extension side spool Se. The valve body 15 is pressed against the flange 122b.
  • the pressure side pressure introduction passage Ip is considered so as not to cause resistance to the flow of the passing liquid.
  • the annular valve body 15 When the pressure side chamber R2 is compressed and the pressure is increased during the contraction operation of the shock absorber D, the annular valve body 15 is pressed by this pressure and is separated from the flange 122b to open the pressure side pressure introduction passage Ip. Further, when the shock absorber D is extended so that the pressure in the extension side back pressure chamber Ce becomes higher than the pressure side chamber R2, it is pressed against the flange 122b to close the pressure side pressure introduction passage Ip, and only the liquid flow from the pressure side chamber R2 is allowed to flow. Allow. As described above, the annular valve body 15 and the spring 16 constitute the pressure-side check valve Tp, and only allow the flow of liquid from the pressure-side chamber R2 toward the extension-side back pressure chamber Ce through the pressure-side pressure introduction passage Ip. It is set as a passage for traffic.
  • the spring 16 plays a role of pressing the annular valve body 15 against the flange 122b, constitutes a compression-side check valve Tp together with the annular valve body 15, and serves to urge the extension-side spool Se toward the extension-side leaf valve Ve. Is also responsible. Therefore, when the extension side leaf valve Ve is bent and the extension side spool Se is pushed down in the direction away from the piston 2 and then the extension side leaf valve Ve is flexed, the extension side spool Se is quickly moved by the spring force of the spring 16. Return to the original position (position shown in FIG. 3).
  • extension side spool Se can be energized by a separate spring, there is an advantage that the compression side check valve Tp and the spring 16 can be shared, the number of parts can be reduced, and the structure can be simplified.
  • the outer diameter of the extension side spool Se is set to be larger than the inner diameter of the annular protrusion 14, and the annular protrusion 14 comes into contact with the extension side annular plate 66.
  • the pressure in the extension side back pressure chamber Ce is always urged toward the extension side leaf valve Ve.
  • the pressure side leaf valve Vp overlaid on the piston 2 has an annular shape to allow the holding shaft 8a of the piston holder 8 to be inserted, as in the extension side leaf valve Ve.
  • it is constituted by one annular plate, it may be constituted by laminating a plurality of annular plates.
  • the pressure side leaf valve Vp comprised in this way is piled up the upper direction in FIG. 3 of the piston 2, and can be attached / detached to the pressure side valve seat 2b and the inner peripheral seat part 2c.
  • the pressure-side leaf valve Vp is provided with a notch Op that functions as an orifice when seated on the pressure-side valve seat 2b on the outer periphery thereof, and is slidably mounted on the outer periphery of the shim 61.
  • a pressure side annular plate 62 that is superimposed on the pressure side leaf valve Vp is slidably mounted.
  • an annular auxiliary valve 81 having an outer diameter smaller than that of the pressure side annular plate 62 is stacked on the pressure side leaf valve side of the pressure side annular plate 62, and this auxiliary valve 81 is also connected to the shim 61. It is slidably mounted on the outer periphery.
  • the axial length when the pressure side leaf valve Vp, the pressure side annular plate 62 and the auxiliary valve 81 are stacked is set to be shorter than the axial length of the shim 61.
  • a pressure side stopper 63 is provided above the shim 61 in FIG. 3 and has an annular shape whose outer diameter is set larger than the inner diameter of the auxiliary valve 81 and the pressure side annular plate 62.
  • the compression side chamber member 11 is overlaid on the upper side. Therefore, the pressure-side leaf valve Vp, the pressure-side annular plate 62, and the auxiliary valve 81 are guided by the shim 61 and can move up and down in FIG. 3, which is the axial direction between the piston 2 and the pressure-side stopper 63. .
  • the pressure-side leaf valve Vp When the pressure-side leaf valve Vp is pressed by pressure from the pressure-side passage 4 side, the outer periphery thereof bends together with the pressure-side annular plate 62, and the pressure-side leaf plate Vp and the auxiliary valve 81 can be moved away from the piston 2 as a whole.
  • the retraction amounts of the pressure side leaf valve Vp, the pressure side annular plate 62 and the auxiliary valve 81 from the piston 2 are set by the length of the shim 61 in the axial direction.
  • the shim 61 since the shim 61 is constituted by a plurality of annular plates, the shim 61 can be adjusted by the number of laminated annular plates, but the shim 61 may be constituted by a single annular plate.
  • the pressure side annular plate 62 is bent and has higher rigidity than the pressure side leaf valve Vp. For this reason, the axial length (thickness) of the compression-side annular plate 62 is longer than the axial length (thickness) of the compression-side leaf valve Vp, but not only the rigidity is increased by the axial length but also the compression-side leaf valve.
  • the compression side annular plate 62 may be formed of a material having higher rigidity than Vp.
  • the inner diameter of the compression side annular plate 62 is set to be smaller than the outer diameter of the inner peripheral sheet portion 2c provided in the piston 2.
  • the outer diameter of the pressure side annular plate 62 is set to be larger than the inner diameter of the pressure side valve seat 2b.
  • the pressure-side back pressure chamber Cp urges the pressure-side spool Sp toward the pressure-side annular plate 62 with the pressure introduced inside. Therefore, the pressure side leaf valve Vp overlapping the pressure side annular plate 62 is urged toward the piston 2 by the urging force received from the pressure side spool Sp and the pressure in the pressure side back pressure chamber Cp.
  • the pressure side annular plate 62 When the pressure side annular plate 62 is pressed from the back side by the pressure in the pressure side back pressure chamber Cp and the pressure side spool Sp, and the pressure side leaf valve Vp is seated on the pressure side valve seat 2b and the inner peripheral seat portion 2c, the pressure side annular plate 62 is The inner circumferential seat portion 2c and the pressure side valve seat 2b are supported. Therefore, the pressure in the pressure side back pressure chamber Cp and the urging force by the pressure side spool Sp are received by the pressure side annular plate 62, the deformation of the pressure side leaf valve Vp is suppressed, and the pressure side leaf valve Vp is not overloaded. ing.
  • the auxiliary valve 81 has an outer diameter smaller than that of the pressure side leaf valve Vp and the pressure side annular plate 62. Therefore, when the pressure side leaf valve Vp and the pressure side annular plate 62 are bent by the pressure of the pressure side passage 4, the outer peripheral side is more easily bent than the auxiliary valve 81, and the auxiliary side valve 81 is used to attenuate the pressure side damping force. You can tune the characteristics. If the auxiliary valve 81 is unnecessary due to the damping characteristic generated in the shock absorber D, it can be omitted. Conversely, a plurality of auxiliary valves 81 may be stacked.
  • the pressure side chamber member 11 is disposed on the side opposite to the piston of the pressure side leaf valve Vp, and is fitted to the outer periphery of the spacer 111 and the cylindrical spacer 111 fitted to the outer periphery of the holding shaft 8 a in the piston holder 8. And a sliding cylinder 112 with which the compression side spool Sp slides.
  • the spacer 111 is mounted on the outer periphery of the holding shaft 8a, and opens from the recess 111a provided on the entire outer periphery of the upper end in FIG. 3, the annular groove 111b provided on the inner periphery, and the annular groove 111b.
  • the slidable contact cylinder 112 includes a cylinder portion 112a in which the compression side spool Sp is slidably contacted on the inner periphery, and a flange 112b protruding from the upper end inner periphery in FIG. 3 of the cylinder portion 112a.
  • the spacer 111 and the sliding contact cylinder 112 are integrated to form an annular recess, and the pressure side back pressure chamber Cp is formed in the annular recess. It is formed.
  • the pressure side chamber member 11 is composed of the spacer 111 and the sliding contact cylinder 112 in order to facilitate processing, but it may be composed of one part.
  • the annular groove 111b on the inner periphery of the spacer 111 faces the groove 8h provided on the holding shaft 8a, and the pressure-side back pressure chamber Cp is grooved through the expansion-side pilot orifice Pe. 8h.
  • the pressure side chamber member 11 is in close contact with the upper end in FIG. 3 in contact with the flange 8 b of the piston holder 8.
  • the groove 8h is formed by the piston 2, shims 61 and 65, the extension side stopper 67 and the compression side stopper 63, the extension side chamber member 12 and the compression side chamber member 11 mounted on the holding shaft 8a, and the extension side chamber R1 and the pressure side chamber R2. Communication has been cut off.
  • the groove 8h communicates with the accommodating portion L through the port 8e, is connected to the adjustment passage Pc, and extends through the compression side pilot orifice Pp and through the expansion side pilot orifice Pe and the compression side back pressure chamber through the extension side pilot orifice Pe. Connected to Cp. As described above, the groove 8h forms a communication path that communicates with the expansion-side back pressure chamber Ce via the compression-side resistance element and also communicates with the compression-side back pressure chamber Cp via the expansion-side resistance element.
  • the pressure side stopper 63 is interposed between the spacer 111 and the shim 61 in the pressure side chamber member 11, but the pressure side stopper 63 is abolished so that the spacer 111 functions as a stopper. You may make it regulate a movement minimum.
  • a compression side spool Sp is accommodated in the sliding contact cylinder 112 in the sliding contact cylinder 112, a compression side spool Sp is accommodated.
  • the pressure side spool Sp is in sliding contact with the inner periphery of the cylindrical portion 112 a of the sliding contact cylinder 112, and can move in the axial direction within the sliding contact cylinder 112.
  • the pressure-side spool Sp includes an annular spool body 17 and an annular protrusion 18 that rises from the outer periphery of the lower end of the spool body 17 in FIG.
  • the inner diameter of the annular protrusion 18 is set to be smaller than the outer diameter of the pressure-side annular plate 62 so that the annular protrusion 18 can come into contact with the upper surface in FIG.
  • the inner diameter of the spool body 17 is larger than the outer diameter of the spacer 111, the inner diameter may be set to a diameter that is in sliding contact with the outer periphery of the spacer 111, and the compression-side back pressure chamber Cp may be sealed with the compression-side spool Sp. Good.
  • the sliding contact cylinder 112 of the compression side chamber member 11 is provided with an expansion side pressure introduction passage Ie that passes through the flange 112b and communicates the compression side back pressure chamber Cp and the expansion side chamber R1.
  • An annular valve body 19 is superimposed on the lower end of the flange 112b of the sliding contact cylinder 112 in FIG. 3, and an annular valve body is provided by a spring 20 interposed between the annular valve body 19 and the spool body 17 of the compression side spool Sp. 19 is pressed against the flange 112b.
  • the extension side pressure introduction passage Ie is considered so as not to cause resistance to the flow of the passing liquid.
  • the annular valve body 19 and the spring 20 constitute the extension-side check valve Te, and only allow the flow of liquid from the extension-side chamber R1 toward the compression-side back pressure chamber Cp through the extension-side pressure introduction passage Ie. It is set as a one-way passage.
  • the spring 20 plays a role of pressing the annular valve body 19 against the flange 112b, constitutes an extension check valve Te together with the annular valve body 19, and plays a role of urging the pressure side spool Sp toward the pressure side leaf valve Vp. Also bears. Therefore, when the pressure-side leaf valve Vp is bent and the pressure-side spool Sp is pushed up in the direction away from the piston 2 and the bending of the pressure-side leaf valve Vp is eliminated, the pressure-side spool Sp is quickly returned to the original position (by the spring force of the spring 20). Return to the position shown in FIG.
  • the pressure side spool Sp can be biased by a separate spring, there is an advantage that the extension side check valve Te and the spring 20 can be shared, the number of parts can be reduced, and the structure can be simplified.
  • the outer diameter of the pressure side spool Sp is set to be larger than the inner diameter of the annular protrusion 18 so that the annular protrusion 18 comes into contact with the pressure side annular plate 62.
  • the pressure in the chamber Cp is always urged toward the compression side leaf valve Vp.
  • the pressure receiving area which receives the pressure of the extension side back pressure chamber Ce of the extension side spool Se is a difference between the area of a circle whose diameter is the outer diameter of the extension side spool Se and the area of the circle whose diameter is the inner diameter of the annular protrusion 14. It becomes.
  • the pressure receiving area that receives the pressure of the pressure side back pressure chamber Cp of the pressure side spool Sp is a difference between the area of the circle having the outer diameter of the pressure side spool Sp as the diameter and the area of the circle having the inner diameter of the annular protrusion 18 as the diameter.
  • the pressure receiving area where the pressure of the expansion side back pressure chamber Ce directly acts on the expansion side annular plate 66 is from the area of a circle whose diameter is the inner diameter of the annular protrusion 14 to the circle whose diameter is the outer diameter of the shim 65. It is the area excluding the area. Therefore, the force obtained by multiplying the area obtained by subtracting the area of the circle having the outer diameter of the shim 65 from the area of the circle having the outer diameter of the extension side spool Se as the diameter of the extension side back pressure chamber Ce is the extension side load. Acting on the extension side leaf valve Ve. The extension side leaf valve Ve is biased toward the piston 2 by the extension side load.
  • extension-side annular plate 66 may be eliminated and the annular protrusion 14 may be brought into direct contact with the back surface of the extension-side leaf valve Ve. Also in this case, since the extension side leaf valve Ve is mounted on the outer periphery of the shim 65, the same extension side load as that when the extension side annular plate 66 is provided acts on the extension side leaf valve Ve.
  • the pressure receiving area where the pressure of the pressure side back pressure chamber Cp directly acts on the pressure side annular plate 62 is the area of the circle whose diameter is the outer diameter of the shim 61 from the area of the circle whose diameter is the inner diameter of the annular protrusion 18. Excluded area. Therefore, the force obtained by multiplying the area obtained by subtracting the area of the circle having the outer diameter of the shim 61 from the area of the circle having the outer diameter of the compression side spool Sp by the pressure of the compression side back pressure chamber Cp as the compression side load is the compression side leaf. Acts on the valve Vp. The pressure side leaf valve Vp is urged toward the piston 2 by the pressure side load.
  • the pressure side annular plate 62 may be eliminated and the annular protrusion 18 may be brought into direct contact with the back surface of the pressure side leaf valve Vp. Also in this case, since the pressure side leaf valve Vp is mounted on the outer periphery of the shim 61, the same pressure side load as when the pressure side annular plate 62 is provided acts on the pressure side leaf valve Vp.
  • the extension side load is increased by the extension side spool Se. It is determined only by the pressure receiving area that receives the pressure of the side back pressure chamber Ce.
  • the pressure side load is the pressure side back pressure chamber of the pressure side spool Sp. It depends only on the pressure receiving area that receives the pressure of Cp.
  • the expansion side load acting on the expansion side leaf valve Ve can be set by the pressure receiving area that receives the pressure in the expansion side back pressure chamber Ce of the expansion side spool Se.
  • the pressure side load acting on the pressure side leaf valve Vp can be set by the pressure receiving area that receives the pressure in the pressure side back pressure chamber Cp of the pressure side spool Sp.
  • the pressure receiving areas of the compression side spool Sp and the expansion side spool Se are made equal, but the difference between the expansion side load and the compression side load can be given by setting the pressure receiving area.
  • an adjustment passage Pc is provided to connect the downstream side of the communication passage formed by the groove 8h that connects the extension side back pressure chamber Ce and the pressure side back pressure chamber Cp, and the upstream side of the extension side discharge passage Ee and the pressure side discharge passage Ep. It has been.
  • An electromagnetic pressure control valve 6 is provided in the middle of the adjustment passage Pc so that the pressures in the upstream extension-side back pressure chamber Ce and the pressure-side back pressure chamber Cp can be controlled.
  • the electromagnetic pressure control valve 6 closes the adjustment passage Pc when not energized and performs pressure control when energized.
  • a fail valve FV that bypasses the electromagnetic pressure control valve 6 is provided in the middle of the adjustment passage Pc.
  • the electromagnetic pressure control valve 6 includes a valve seat member 30 including a valve housing cylinder 30a and a control valve valve seat 30d, and an electromagnetic valve valve body that is attached to and detached from the control valve valve seat 30d. 31 and a solenoid Sol that applies thrust to the solenoid valve body 31 and drives it in the axial direction.
  • valve seat member 30 is fitted into the socket 8c of the piston holder 8, and the diameter of the valve seat member 30 is inserted by inserting the valve housing cylinder 30a into the inner periphery of the annular valve housing 32 that is superimposed on the upper end of the flange 8b in FIG. It is accommodated in the accommodating part L, being positioned in the direction.
  • the valve housing 32 has an annular shape, an annular window 32a provided at the upper end in FIG. 2, a port 32b that opens from the annular window 32a and communicates with the lower end in FIG. 2, and an upper end in FIG.
  • a notch groove 32c that opens from the inner periphery and communicates with the port 32b, a vertical groove 32d that is provided on the outer periphery and extends along the axial direction, and an annular fail valve seat 32e that surrounds the outer periphery of the annular window 32a. Configured.
  • the port 32b faces the opening facing the upper end of the flange 8b of the port 8e, and the port 32b and the cutout groove 32c have the port 8e. Further, the vertical groove 32d is communicated with the notch 8g provided in the flange 8b.
  • the port 32b and the notch groove 32c are communicated with the groove 8h forming the communication path through the port 8e, and further, the expansion side back pressure chamber Ce and the pressure side back pressure are connected via the expansion side pilot orifice Pe and the pressure side pilot orifice Pp. It communicates with the chamber Cp. Further, the vertical groove 32d communicates with the pressure side chamber R2 through the expansion side discharge passage Ee formed by the notch 8g, the vertical hole 8d, and the check valve 25, and the through hole 9c, the recess 8i, the through hole 8j, and the check.
  • the pressure side discharge passage Ep formed by the valve 22 communicates with the extension side chamber R1.
  • valve accommodating cylinder 30a in the cylindrical valve seat member 30 is accommodated.
  • the valve seat member 30 has a bottomed cylindrical shape and has a valve accommodating cylinder 30a having a flange 30b on the outer periphery of the upper end in FIG. 2, a through hole 30c that opens from the side of the valve accommodating cylinder 30a and communicates with the inside,
  • An annular control valve seat 30d that protrudes in the axial direction is provided at the upper end in FIG. 2 of the valve housing cylinder 30a.
  • a fail valve body 33 which is an annular leaf valve is mounted on the outer periphery of the valve housing cylinder 30a of the valve seat member 30, a fail valve body 33 which is an annular leaf valve is mounted.
  • the fail valve body 33 has an inner periphery that is the flange 30b of the valve seat member 30 and the upper end of the valve housing 32 in FIG. It is clamped by the inner periphery and fixed. Therefore, the fail valve body 33 is seated in the state where the initial deflection is given to the annular fail valve seat 32e provided on the valve housing 32 on the outer peripheral side, and closes the annular window 32a.
  • the fail valve body 33 bends when the pressure acting in the annular window 32a through the port 32b reaches the valve opening pressure, opens the annular window 32a, and connects the port 32b to the extension side discharge passage Ee and the pressure side discharge passage Ep. Communicate.
  • a fail valve FV is formed by the fail valve body 33 and the fail valve seat 32e.
  • valve housing cylinder 30a When the valve housing cylinder 30a is inserted into the valve housing 32 and the valve seat member 30 is assembled to the valve housing 32, the notch groove 32c provided in the valve housing 32 faces the through hole 30c provided in the valve housing cylinder 30a.
  • the extension-side back pressure chamber Ce and the compression-side back pressure chamber Cp are communicated with each other in the valve housing cylinder 30a through the port 32b.
  • valve fixing member 35 that is annular and contacts the upper end of the flange 30b in FIG. 1 is stacked above the valve seat member 30 in FIG.
  • a solenoid Sol accommodated in the valve accommodating cylinder 9 is disposed.
  • the valve fixing member 35 has a notch groove 35 a so that the inner circumferential space of the valve fixing member 35 can communicate with the outer circumferential space of the valve seat member 30 even when abutting against the flange 30 b of the valve seat member 30. Is provided. This communication may be performed not by the notch groove 35a but by a hole such as a port.
  • the solenoid Sol is a top-cylindrical molded stator 36 in which a winding 37 and a harness H that energizes the winding 37 are integrated with a mold resin, and a top-cylindrical cylindrical stator that is fitted to the inner periphery of the mold stator 36.
  • the first fixed iron core 38, the annular second fixed iron core 39 superimposed on the lower end in FIG. 1 of the molded stator 36, and the first fixed iron core 38 and the second fixed iron core 39 are magnetically interposed. Fixed to the inner periphery of the movable core 41, the filler ring 40 that forms a gap, the cylindrical movable core 41 that is axially movable on the inner peripheral side of the first fixed core 38 and the second fixed core 39.
  • the solenoid Sol attracts the movable iron core 41 by energizing the winding 37 and applies a downward thrust to the shaft 42 in FIG.
  • the shaft 42 is in contact with the electromagnetic valve body 31, and the solenoid Sol applies a downward thrust in FIG. 2 to the electromagnetic valve body 31 when energized.
  • a solenoid valve body 31 is slidably inserted into the valve seat member 30.
  • the solenoid valve body 31 is provided on the side of the valve seat member 30 that is slidably inserted into the valve housing cylinder 30a of the valve seat member 30 and the counter valve seat member side that is the upper side of the small diameter portion 31a in FIG.
  • the solenoid valve body 31 is formed with the large-diameter portion 31b with the outer diameter on the side opposite to the valve seat member larger than the small-diameter portion 31a with the recess 31c as a boundary.
  • the electromagnetic valve body 31 includes a seating portion 31g facing the control valve valve seat 30d at the lower end in FIG. 2 of the large-diameter portion 31b, and the seating portion 31g is controlled when moved in the axial direction with respect to the valve seat member 30.
  • the valve seat 30d is detached and seated. That is, the electromagnetic pressure control valve 6 includes the electromagnetic valve body 31 and the valve seat member 30. When the seating portion 31g is seated on the control valve valve seat 30d, the electromagnetic pressure control valve 6 is closed.
  • a coil spring 34 is interposed between the flange 30b of the valve seat member 30 and the spring receiving portion 31d to urge the electromagnetic valve valve body 31 in a direction away from the valve seat member 30. Therefore, the electromagnetic valve body 31 is always urged in the direction away from the valve seat member 30 by the coil spring 34, and if a thrust force against the coil spring 34 from the solenoid Sol does not act, It is positioned at the most distant position.
  • the coil spring 34 is used to urge the solenoid valve valve body 31 in the direction away from the valve seat member 30, but the urging force can be exerted in addition to the coil spring 34.
  • An elastic body that can be used can be used.
  • the solenoid valve body 31 When the solenoid valve body 31 is farthest from the valve seat member 30, the small diameter portion 31a is opposed to the through hole 30c to close the through hole 30c.
  • the solenoid Sol When the solenoid Sol is energized to move the solenoid valve valve 31 by a predetermined amount from the position farthest away from the valve seat member 30 to the valve seat member 30 side, the solenoid valve valve 31 always places the recess 31c into the through hole 30c.
  • the through holes 30c are opened so as to face each other.
  • the solenoid valve body 31 opens the through hole 30c and the seating portion 31g is separated from the control valve valve seat 30d, the through hole 30c passes through the recess 31c of the solenoid valve valve body 31 and the notch groove 35a provided in the valve fixing member 35.
  • the expansion side discharge passage Ee and the pressure side discharge passage Ep are communicated.
  • the pressure on the upstream side of the electromagnetic pressure control valve 6 can be controlled according to the thrust of the solenoid Sol. Since the upstream side of the electromagnetic pressure control valve 6 communicates with the expansion side back pressure chamber Ce and the pressure side back pressure chamber Cp via the adjustment passage Pc, the electromagnetic pressure control valve 6 causes the expansion side back pressure chamber Ce and the pressure side to communicate with each other. The pressure in the back pressure chamber Cp can be controlled. Therefore, the expansion side load and the compression side load can be controlled by adjusting the pressures of the expansion side back pressure chamber Ce and the compression side back pressure chamber Cp according to the energization amount to the solenoid Sol.
  • the downstream side of the electromagnetic pressure control valve 6 communicates with the expansion side discharge passage Ee and the pressure side discharge passage Ep, and the liquid that has passed through the electromagnetic pressure control valve 6 causes the pressure side chamber R2 on the low pressure side during the expansion operation of the shock absorber D.
  • the shock absorber D When the shock absorber D is contracted, it is discharged into the low-pressure side expansion chamber R1. Therefore, the adjustment passage Pc is formed by the port 8e, the port 32b, the notch groove 32c, a part of the accommodating portion L, and the vertical groove 32d.
  • the electromagnetic pressure control valve 6 has a blocking position in which the through hole 30c in the valve seat member 30 is closed by the small diameter portion 31a in the electromagnetic valve body 31 during a failure in which the solenoid Sol cannot be energized. Therefore, the electromagnetic pressure control valve 6 functions not only as a pressure control valve but also as an on-off valve.
  • the fail valve FV opens and closes an annular window 32a that communicates with the port 32b, and the valve opening pressure is set to a pressure that exceeds the upper limit pressure that can be controlled by the electromagnetic pressure control valve 6.
  • the electromagnetic pressure control valve 6, the port 32b is communicated with the expansion side discharge passage Ee and the pressure side discharge passage Ep.
  • the fail valve FV is opened, and the pressures in the extension-side back pressure chamber Ce and the pressure-side back pressure chamber Cp are opened.
  • the valve pressure can be controlled. Therefore, for example, when the electromagnetic pressure control valve 6 is in the shut-off position at the time of failure, the pressures in the extension side back pressure chamber Ce and the pressure side back pressure chamber Cp are controlled to the valve opening pressure of the fail valve FV.
  • a space K is formed in the valve housing cylinder 30a and on the tip side from the through hole 30c.
  • the space K communicates with the outside of the solenoid valve valve body through a communication path 31e provided in the solenoid valve valve body 31 and an orifice 31f.
  • the liquid in the extension side chamber R1 pushes open the extension side check valve Te, passes through the extension side pressure introduction passage Ie, and flows into the adjustment passage Pc.
  • the liquid that has passed through the adjustment passage Pc pushes the check valve 25 open and is discharged to the low pressure side pressure side chamber R2 through the extension side discharge passage Ee.
  • the expansion side pilot orifice Pe gives a resistance when the liquid passes and causes a pressure loss. Since the liquid is flowing, the expansion side pilot orifice Pe has a lower pressure than the expansion side chamber R1 downstream of the adjustment passage Pc.
  • the check valve 22 provided on Ep remains closed without opening.
  • the expansion-side pressure introduction passage Ie not only communicates with the compression-side back pressure chamber Cp but also communicates with the expansion-side back pressure chamber Ce through the groove 8h, but the compression-side pressure introduction passage Ip is closed by the compression-side check valve Tp. Therefore, when the shock absorber D is extended, the pressure in the extension side back pressure chamber Ce is higher than that of the compression side chamber R2.
  • the pressure in the pressure side back pressure chamber Cp is higher than that in the pressure side chamber R2 on the low pressure side, but there is no inconvenience because it only energizes the pressure side leaf valve Vp that closes the pressure side passage 4 where no liquid flows. .
  • the electromagnetic pressure control valve 6 is provided in the adjustment passage Pc, and if the solenoid Sol of the electromagnetic pressure control valve 6 is energized to control the pressure on the upstream side of the adjustment passage Pc, the extension side back pressure is increased.
  • the extension side load can be controlled to a desired load by adjusting the pressure in the chamber Ce.
  • the extension side load controlled by the electromagnetic pressure control valve 6 acts in the valve closing direction, and the pressure in the extension side chamber R1 acts in the valve opening direction through the extension side passage 3.
  • the extension-side leaf valve Ve opens when the extension-side load exceeds the force due to the action of the pressure in the extension-side chamber R1, and slides on the outer periphery of the shim 65 to a position where the two balance each other and retracts from the piston 2.
  • the retraction amount by which the extension-side leaf valve Ve is separated from the piston 2 is determined according to the extension-side load. Therefore, the retraction amount can be controlled according to the energization amount to the solenoid Sol.
  • the opening degree of the extension side leaf valve Ve can be controlled by the electromagnetic pressure control valve 6, and thereby the extension side damping force when the buffer D is extended can be adjusted in magnitude.
  • the liquid in the pressure side chamber R2 pushes and opens the pressure side check valve Tp, passes through the pressure side pressure introduction passage Ip, and flows to the adjustment passage Pc.
  • the liquid that has passed through the adjustment passage Pc pushes the check valve 22 open and is discharged to the low-pressure-side extension side chamber R1 through the pressure-side discharge passage Ep.
  • the pressure side pilot orifice Pp provides resistance when the liquid passes and causes a pressure loss. In the state where the liquid flows, the pressure side pilot orifice Pp has a pressure lower than the pressure side chamber R2 downstream of the adjustment passage Pc.
  • the check valve 25 provided at Ee is not opened and remains closed.
  • the compression-side pressure introduction passage Ip not only communicates with the expansion-side back pressure chamber Ce but also communicates with the compression-side back pressure chamber Cp through the groove 8h, but the expansion-side pressure introduction passage Ie is blocked by the expansion-side check valve Te. Therefore, the pressure in the compression side back pressure chamber Cp becomes higher than that of the expansion side chamber R1 when the shock absorber D is contracted.
  • the pressure in the extension side back pressure chamber Ce is higher than that in the extension side chamber R1 on the low pressure side, but it only energizes the extension side leaf valve Ve that closes the extension side passage 3 where no liquid flows. There is no inconvenience.
  • the pressure side load valve controlled by the electromagnetic pressure control valve 6 acts on the pressure side leaf valve Vp in the valve closing direction, and the pressure in the pressure side chamber R2 acts on the pressure side passage 4 in the valve opening direction.
  • the pressure-side leaf valve Vp opens when the force due to the action of the pressure in the pressure-side chamber R2 exceeds the pressure-side load, slides on the outer periphery of the shim 61 to a position where both balance, and moves backward from the piston 2.
  • the retraction amount by which the pressure-side leaf valve Vp is separated from the piston 2 is determined according to the pressure-side load. Therefore, the retraction amount can be controlled according to the energization amount to the solenoid Sol.
  • the opening degree of the pressure side leaf valve Vp can be controlled by the electromagnetic pressure control valve 6, whereby the pressure side damping force when the shock absorber D is contracted can be adjusted in magnitude.
  • the outer diameter of the extension side leaf valve Ve is smaller than the outer diameter of the compression side leaf valve Vp, and receives the pressure of the extension side chamber R1 of the extension side leaf valve Ve.
  • the pressure receiving area is smaller than the pressure receiving area that receives the pressure of the pressure side chamber R2 of the pressure side leaf valve Vp. Therefore, even if the extension side load and the compression side load are the same in the electromagnetic pressure control valve 6, the valve opening pressure of the extension side leaf valve Ve becomes larger than the valve opening pressure of the compression side leaf valve Vp, and the extension side damping force is reduced to the compression side. Can be greater than force.
  • the communication path that communicates the extension-side back pressure chamber Ce and the pressure-side back pressure chamber Cp is provided on the outer periphery of the holding shaft 8a of the piston holder 8, and therefore communicates with the holding shaft 8a.
  • a separator is not required for forming the communication path, the number of parts can be reduced, the cost can be reduced, and the separator 8 is not provided in the holding shaft 8a, so the diameter of the vertical hole 8d can be reduced. Since the diameter can be reduced, the strength of the piston holder 8 can be secured.
  • the groove 8h is not connected to the expansion side pressure introduction passage Ie and the pressure side pressure introduction passage Ip by the above-described components including the piston 2 assembled to the holding shaft 8a. Closed to prevent communication.
  • Each of the components assembled to the holding shaft 8a is fixed to the holding shaft 8a in close contact with the load in the axial direction by the spacer 121 functioning as a piston nut, so that the groove 8h can be closed tightly. Therefore, in the shock absorber D of the present invention, since the liquid does not leak from the groove 8h functioning as the communication path to the extension side chamber R1 or the pressure side chamber R2, the problem that the damping force characteristic varies for each product is solved.
  • the cross-sectional shape of the groove 8h forming the communication path can be designed arbitrarily.
  • the communication path is formed by a groove 8h provided on the outer periphery of the holding shaft 8a.
  • a gap that forms the communication path is formed between the holding shaft 8a and the parts assembled to the holding shaft 8a. Therefore, for example, a chamfer along the axial direction is formed on the outer periphery of the holding shaft 8a, and a gap is provided between each part assembled to the holding shaft 8a at this chamfered portion to provide a communication path. It may be formed. Even if it does in this way, the effect similar to the case where a communicating path is formed in the groove
  • channel 8h is acquired.
  • the expansion side pilot orifice (extension side resistance element) Pe is provided in the compression side chamber member 11
  • the compression side pilot orifice (pressure side resistance element) Pp is provided in the expansion side chamber member 12.
  • the expansion resistance element and the compression resistance element are provided on the piston holder side, for example, when there are four types of expansion resistance elements and compression resistance elements, respectively, in order to realize all these combinations, the total 16 different piston holders had to be prepared.
  • the extension side resistance element and the compression side resistance element are separately provided in the corresponding extension side chamber member 12 and compression side chamber member 11, four types of extension side chamber member 12 and compression side chamber member 11 are prepared. All you need to do is Therefore, when the shock absorber D is configured in this manner, tuning of the extension side resistance element and the compression side resistance element is facilitated, the number of parts to be managed is reduced, and the cost can be further reduced.
  • the holding shaft 8a of the piston holder 8 is provided with a vertical hole 8d communicating with the compression side chamber R2, and an expansion side discharge passage Ee is formed, and the adjustment passage Pc is formed in the vertical hole 8d.
  • a pipe 25a that functions as a valve seat for the check valve 25 that allows only the flow of liquid from the pressure side chamber R2 is provided.
  • the extension side leaf valve Ve and the pressure side leaf valve Vp are slidably fitted to the outer circumferences of the shims 65 and 61, respectively, so that they can be separated from the piston 2.
  • a structure in which the inner peripheral side is fixed to the holding shaft 8a may be employed.
  • the electromagnetic pressure control valve 6 is not limited to the above-described specific structure because it only needs to be able to adjust the pressure in the extension side back pressure chamber Ce and the pressure side back pressure chamber Cp.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

In the shock absorber (D) of the present invention, a communication channel (8h), which allows communication between an extension-side back-pressure chamber (Ce) that urges an extension-side spool (Se) toward an extension-side leaf valve (Ve) and a pressure-side back-pressure chamber (Cp) that urges a pressure-side spool (Sp) toward a pressure-side leaf valve (Vp), is formed in the outer periphery of a holding shaft (8a).

Description

緩衝器Shock absorber
　この発明は、緩衝器に関する。 This invention relates to a shock absorber.
　車両のサスペンションに用いられる緩衝器には、減衰力を可変にできる減衰バルブを備えているものがある。このような緩衝器は、シリンダと、シリンダ内を伸側室と圧側室とに区画するピストンと、一端がピストンに連結されてシリンダ内に移動自在に挿入されるピストンロッドと、減衰バルブを備えて構成される。 Some shock absorbers used in vehicle suspensions have a damping valve that can vary the damping force. Such a shock absorber includes a cylinder, a piston that divides the cylinder into an extension side chamber and a pressure side chamber, a piston rod that is connected to the piston at one end and is movably inserted into the cylinder, and a damping valve. Composed.
　減衰バルブは、たとえば、ＪＰ２０１５－０７２０４７Ａに開示されているように、ピストンに設けられた伸側室と圧側室とを連通する伸側通路と圧側通路を、伸側通路と圧側通路とをそれぞれ開閉する伸側リーフバルブと圧側リーフバルブと、伸側リーフバルブと圧側リーフバルブをそれぞれ押圧する伸側スプールと圧側スプールと、内部圧力で伸側スプールと圧側スプールを押圧する伸側背圧室と圧側背圧室の圧力を調節する電磁圧力制御弁とを備えている。 For example, as disclosed in JP2015-072047A, the damping valve opens and closes an extension side passage and a pressure side passage, which communicate with the extension side chamber and the pressure side chamber provided in the piston, and opens and closes the extension side passage and the pressure side passage, respectively. The expansion side leaf valve, the compression side leaf valve, the expansion side spool and the compression side spool that press the expansion side leaf valve and the compression side leaf valve, respectively, the expansion side back pressure chamber and the compression side back that press the expansion side spool and the compression side spool with internal pressure And an electromagnetic pressure control valve for adjusting the pressure in the pressure chamber.
　このように構成された緩衝器にあっては、単一の電磁圧力制御弁によって伸側背圧室および圧側背圧室内の圧力を制御して、伸長時と収縮時の減衰力を制御できる。 In the shock absorber configured as described above, the damping force at the time of expansion and contraction can be controlled by controlling the pressure in the expansion-side back pressure chamber and the pressure-side back pressure chamber by a single electromagnetic pressure control valve.
　従来の緩衝器にあっては、単一の電磁圧力制御弁によって伸側背圧室と圧側背圧室の圧力を制御するために、伸側背圧室と圧側背圧室とを連通路で連通し、連通路を電磁圧力制御弁へ連通するようにしている。 In the conventional shock absorber, in order to control the pressure in the extension side back pressure chamber and the pressure side back pressure chamber by a single electromagnetic pressure control valve, the extension side back pressure chamber and the pressure side back pressure chamber are connected by a communication path. The communication passage communicates with the electromagnetic pressure control valve.
　この連通路は、ピストンを保持するピストンホルダにおける保持軸に縦孔を設けて、この縦孔にパイプ状のセパレータを挿入して、セパレータの外周に形成される環状隙間によって形成されている。 This communication path is formed by an annular gap formed on the outer periphery of the separator by providing a vertical hole in the holding shaft of the piston holder that holds the piston, and inserting a pipe-shaped separator into the vertical hole.
　このように、従来の緩衝器では、連通路を形成するのに加工が必要なセパレータが必須であって、部品点数が多く、コストが嵩んでしまう。 Thus, in the conventional shock absorber, a separator that needs to be processed is necessary to form the communication path, and the number of parts is large, resulting in an increase in cost.
　また、保持軸に縦孔を設けてセパレータを挿入する関係上、どうしてもピストンホルダの強度が低下してしまう。 Also, the strength of the piston holder is inevitably lowered due to the fact that a vertical hole is provided in the holding shaft and the separator is inserted.
　そこで、本発明は、部品点数を削減でき、かつ、ピストンホルダの強度も確保できる緩衝器の提供を目的とする。 Therefore, an object of the present invention is to provide a shock absorber capable of reducing the number of parts and ensuring the strength of the piston holder.
　本発明における緩衝器にあっては、伸側スプールを伸側リーフバルブへ向けて附勢する伸側背圧室と圧側スプールを圧側リーフバルブへ向けて附勢する圧側背圧室とを連通する連通路が保持軸の外周に形成されているので、保持軸内に連通路を設けるためのセパレータを設ける必要がない。 In the shock absorber according to the present invention, the expansion-side back pressure chamber that urges the expansion-side spool toward the expansion-side leaf valve and the compression-side back pressure chamber that urges the compression-side spool toward the compression-side leaf valve communicate with each other. Since the communication path is formed on the outer periphery of the holding shaft, there is no need to provide a separator for providing the communication path in the holding shaft.
図１は、一実施の形態における緩衝器の断面図である。FIG. 1 is a cross-sectional view of a shock absorber according to an embodiment. 図２は、一実施の形態における緩衝器の電磁圧力制御弁の拡大断面図である。FIG. 2 is an enlarged cross-sectional view of the electromagnetic pressure control valve of the shock absorber in one embodiment. 図３は、一実施の形態における緩衝器のピストン部の拡大断面図である。FIG. 3 is an enlarged cross-sectional view of the piston portion of the shock absorber according to the embodiment.
　以下に、図示した実施の形態に基づいて、この発明を説明する。一実施の形態における緩衝器Ｄは、図１に示すように、シリンダ１と、シリンダ１内に摺動自在に挿入される環状のピストン２と、ピストン２に設けた伸側通路３を開閉する伸側リーフバルブＶｅと、ピストン２に設けた圧側通路４を開閉する圧側リーフバルブＶｐと、伸側チャンバ部材１２および伸側スプールＳｅと、圧側チャンバ部材１１および圧側スプールＳｐと、ピストンホルダ８と、連通路として機能する溝８ｈと、伸側抵抗要素としての伸側パイロットオリフィスＰｅと、圧側抵抗要素としての圧側パイロットオリフィスＰｐと、溝８ｈに接続される調節通路Ｐｃと、調節通路Ｐｃから伸側室Ｒ１へ向かう液体の流れのみを許容する圧側排出通路Ｅｐと、調節通路Ｐｃから圧側室Ｒ２へ向かう液体の流れのみを許容する伸側排出通路Ｅｅと、調節通路Ｐｃに設けられて調節通路Ｐｃの上流圧力を制御する電磁圧力制御弁６とを備えて構成されている。 Hereinafter, the present invention will be described based on the illustrated embodiment. As shown in FIG. 1, the shock absorber D in one embodiment opens and closes a cylinder 1, an annular piston 2 that is slidably inserted into the cylinder 1, and an extension-side passage 3 provided in the piston 2. An extension side leaf valve Ve, a pressure side leaf valve Vp that opens and closes a pressure side passage 4 provided in the piston 2, an extension side chamber member 12 and an extension side spool Se, a pressure side chamber member 11 and a pressure side spool Sp, and a piston holder 8 The groove 8h functioning as a communication path, the expansion pilot orifice Pe as the expansion resistance element, the compression pilot orifice Pp as the compression resistance element, the adjustment path Pc connected to the groove 8h, and the adjustment path Pc A pressure side discharge passage Ep that allows only the flow of liquid toward the side chamber R1, and an extension side discharge that allows only the flow of liquid from the adjustment passage Pc to the pressure side chamber R2. And road Ee, is constituted by an electromagnetic pressure control valve 6 provided in the regulation passage Pc to control the upstream pressure regulating passage Pc.
　以下、緩衝器Ｄの各部について詳細に説明する。シリンダ１は、内部が作動油などの液体で満たされており、図示はしないが下端が閉塞されており、上端には、環状のロッドガイドが装着されている。また、シリンダ１の図１中の下方には、図示はしないが、シリンダ１内を摺動するフリーピストンが設けられており、このフリーピストンによってシリンダ１内に気体室が形成される。なお、シリンダ１内に満たされる液体は、作動油の他、減衰力の発揮が可能な液体であれば使用可能である。 Hereinafter, each part of the shock absorber D will be described in detail. The cylinder 1 is filled with a liquid such as hydraulic oil, the lower end is closed, although not shown, and an annular rod guide is attached to the upper end. A free piston that slides in the cylinder 1 is provided below the cylinder 1 in FIG. 1, and a gas chamber is formed in the cylinder 1 by the free piston. In addition, the liquid with which the cylinder 1 is filled can be used if it is a liquid which can exhibit damping force besides hydraulic oil.
　ピストン２は、シリンダ１内に摺動自在に挿入されていて、シリンダ１内を液体が充填される伸側室Ｒ１と圧側室Ｒ２とを区画しており、シリンダ１内に移動自在に挿通されたピストンロッド７の一端に連結されている。ピストンロッド７は、シリンダ１の上端部に設けた図外の前記ロッドガイドの内周に挿通されてシリンダ１外へ突出している。なお、ピストンロッド７とシリンダ１との間は図示しないシールが設けられていて、シリンダ１内は液密状態とされている。図示したところでは、緩衝器Ｄがいわゆる片ロッド型に設定されているため、緩衝器Ｄの伸縮に伴ってシリンダ１内に出入りするピストンロッド７の体積は、前記した気体室内の気体の体積が膨張あるいは収縮して、前記フリーピストンがシリンダ１内を上下方向に移動して補償されるようになっている。このように緩衝器Ｄは、単筒型に設定されているが、フリーピストン及び気体室の設置に変えて、シリンダ１の外周や外部にリザーバを設けて当該リザーバによって前記ピストンロッド７の体積補償を行ってもよい。 The piston 2 is slidably inserted into the cylinder 1, and defines an extension side chamber R1 and a pressure side chamber R2 filled with liquid in the cylinder 1, and is movably inserted into the cylinder 1. It is connected to one end of the piston rod 7. The piston rod 7 is inserted through the inner periphery of the rod guide (not shown) provided at the upper end of the cylinder 1 and protrudes outside the cylinder 1. A seal (not shown) is provided between the piston rod 7 and the cylinder 1, and the cylinder 1 is in a liquid-tight state. Since the shock absorber D is set to a so-called single rod type, the volume of the piston rod 7 that enters and exits the cylinder 1 as the shock absorber D expands and contracts is the volume of the gas in the gas chamber described above. By expanding or contracting, the free piston moves up and down in the cylinder 1 to be compensated. As described above, the shock absorber D is set to a single cylinder type, but instead of installing a free piston and a gas chamber, a reservoir is provided on the outer periphery or outside of the cylinder 1 and the volume compensation of the piston rod 7 is performed by the reservoir. May be performed.
　ピストンロッド７は、この場合、ピストン２を保持するピストンホルダ８と、一端がピストンホルダ８に連結されてピストンホルダ８とともに電磁圧力制御弁６を収容する中空な収容部Ｌを形成する電磁弁収容筒９と、一端が電磁弁収容筒９に連結されるとともに他端がシリンダ１の上端から外方へ突出するロッド部材１０とで形成されている。 In this case, the piston rod 7 has a piston holder 8 that holds the piston 2 and an electromagnetic valve housing that forms a hollow housing portion L that is connected to the piston holder 8 and that houses the electromagnetic pressure control valve 6 together with the piston holder 8. A cylinder 9 and a rod member 10 having one end connected to the solenoid valve housing cylinder 9 and the other end protruding outward from the upper end of the cylinder 1 are formed.
　ピストンホルダ８は、外周に環状のピストン２が装着される保持軸８ａと、保持軸８ａの図１中上端外周に設けたフランジ８ｂと、フランジ８ｂの図１中上端外周に設けた筒状のソケット８ｃとを備えている。また、ピストンホルダ８は、保持軸８ａの先端から開口して軸方向に伸び前記ソケット８ｃ内に通じる縦孔８ｄと、フランジ８ｂを貫いてソケット８ｃ内に通じるポート８ｅと、保持軸８ａの図１中下端外周に設けた螺子部８ｆと、フランジ８ｂの上端に形成されて縦孔８ｄに通じる切欠８ｇと、保持軸８ａの外周であって螺子部８ｆの図１中上端である終端から根元まで軸方向に沿って形成した溝８ｈと、ソケット８ｃの図１中上端外周に設けた環状の凹部８ｉと、ソケット８ｃに設けられて凹部８ｉからソケット８ｃ内に通じる貫通孔８ｊとを備えて構成されている。 The piston holder 8 includes a holding shaft 8a on which the annular piston 2 is mounted on the outer periphery, a flange 8b provided on the outer periphery of the upper end of the holding shaft 8a in FIG. 1, and a cylindrical shape provided on the outer periphery of the upper end of the flange 8b in FIG. And a socket 8c. The piston holder 8 is opened from the tip of the holding shaft 8a, extends in the axial direction, communicates with the socket 8c, a port 8e that passes through the flange 8b and communicates with the socket 8c, and a diagram of the holding shaft 8a. 1 screw portion 8f provided at the outer periphery of the lower end of the middle 1, a notch 8g formed at the upper end of the flange 8b and leading to the vertical hole 8d, and the outer periphery of the holding shaft 8a and the end of the screw portion 8f at the upper end in FIG. A groove 8h formed along the axial direction, an annular recess 8i provided on the outer periphery of the upper end in FIG. 1 of the socket 8c, and a through hole 8j provided in the socket 8c and leading from the recess 8i into the socket 8c. It is configured.
　電磁弁収容筒９は、有頂筒状の収容筒部９ａと、収容筒部９ａよりも外径が小径であって当該収容筒部９ａの頂部から図１中上方へ伸びる筒状の連結部９ｂと、収容筒部９ａの側方から開口して内部へ通じる透孔９ｃとを備えて構成されている。そして、電磁弁収容筒９の収容筒部９ａの内周にピストンホルダ８のソケット８ｃを螺着して、電磁弁収容筒９にピストンホルダ８を一体化すると、電磁弁収容筒９とピストンホルダ８とで収容筒部９ａ内に電磁圧力制御弁６が収容される収容部Ｌが形成される。また、収容部Ｌは、調節通路Ｐｃの一部として機能しており、前記したポート８ｅを介して保持軸８ａの外周に設けた溝８ｈに連通されるとともに、伸側排出通路Ｅｅを形成する縦孔８ｄを通じて圧側室Ｒ２に連通される。 The solenoid valve housing cylinder 9 includes a top-cylindrical housing cylinder portion 9a and a cylindrical connecting portion that has an outer diameter smaller than that of the housing cylinder portion 9a and extends upward from the top of the housing cylinder portion 9a in FIG. 9b and a through-hole 9c that opens from the side of the accommodating tube portion 9a and communicates with the inside. Then, when the socket 8c of the piston holder 8 is screwed to the inner periphery of the accommodating cylinder portion 9a of the electromagnetic valve accommodating cylinder 9 and the piston holder 8 is integrated with the electromagnetic valve accommodating cylinder 9, the electromagnetic valve accommodating cylinder 9 and the piston holder are integrated. 8, the accommodating part L in which the electromagnetic pressure control valve 6 is accommodated is formed in the accommodating cylinder part 9a. The accommodating portion L functions as a part of the adjustment passage Pc, communicates with the groove 8h provided on the outer periphery of the holding shaft 8a via the port 8e, and forms the extension-side discharge passage Ee. The pressure side chamber R2 communicates with the vertical hole 8d.
　前記したように電磁弁収容筒９にピストンホルダ８が一体化されると、透孔９ｃが凹部８ｉに対向して、貫通孔８ｊと協働して、収容部Ｌを伸側室Ｒ１に連通させるようになっている。また、ソケット８ｃの図１中上端外周に設けた凹部８ｉには、環状弁体２２ａが装着されており、この環状弁体２２ａが図１中上方からばね２２ｂによって附勢されて、貫通孔８ｊを開閉するようになっている。この環状弁体２２ａとばね２２ｂは、逆止弁２２を構成している。圧側排出通路Ｅｐは、本例では、透孔９ｃ、凹部８ｉ、貫通孔８ｊによって形成されており、前記した逆止弁２２によって、調節通路Ｐｃから伸側室Ｒ１へ向かう液体の流れのみを許容し、逆向きの液体の流れを阻止する。 As described above, when the piston holder 8 is integrated with the solenoid valve housing cylinder 9, the through hole 9c faces the recess 8i, and cooperates with the through hole 8j to allow the housing portion L to communicate with the extension side chamber R1. It is like that. Further, an annular valve body 22a is attached to the recess 8i provided on the outer periphery of the upper end in FIG. 1 of the socket 8c. The annular valve body 22a is urged by a spring 22b from above in FIG. Open and close. The annular valve body 22 a and the spring 22 b constitute a check valve 22. In this example, the pressure-side discharge passage Ep is formed by a through-hole 9c, a recess 8i, and a through-hole 8j, and only the flow of liquid from the adjustment passage Pc to the extension-side chamber R1 is allowed by the check valve 22 described above. Block the flow of liquid in the opposite direction.
　前述の保持軸８ａに設けた縦孔８ｄは、伸側排出通路Ｅｅとして機能しており、保持軸８ａに設けた縦孔８ｄ内には、収容部Ｌから縦孔８ｄを通じて圧側室Ｒ２へ向かう液体の流れのみを許容する逆止弁２５が設けられている。この逆止弁２５は、縦孔８ｄ内に装着されるパイプ２５ａと、パイプ２５ａに嵌合されるカップ状のばね受２５ｂと、パイプ２５ａの端部に着座するとともにばね受２５ｂ内に収容される円盤状の弁体２５ｃと、ばね受２５ｂの頂部と弁体２５ｃとの間に介装されるばね２５ｄとを備えて構成されている。ばね受２５ｂには切欠が設けてあって、パイプ２５ａから弁体２５ｃが離座すると、逆止弁２５が開弁して、縦孔８ｄ側から圧側室Ｒ２へ向かう液体の流れを許容する。これに対して、反対の液体の流れに対しては、弁体２５ｃがパイプ２５ａの図１中下端に当接して逆止弁２５が閉弁して液体の流れを阻止する。このように逆止弁２５は、アッセンブリ化されて縦孔８ｄ内に収容されており、縦孔８ｄの出口近傍に嵌合される皿ばねによって、縦孔８ｄに固定される。よって、伸側排出通路Ｅｅは、圧側室Ｒ２から調節通路Ｐｃへ向かう液体の流れを阻止するとともに、調節通路Ｐｃから圧側室Ｒ２へ向かう液体の流れのみを許容するようになっている。 The above-described vertical hole 8d provided in the holding shaft 8a functions as the extension side discharge passage Ee, and the vertical hole 8d provided in the holding shaft 8a goes from the accommodating portion L to the compression side chamber R2 through the vertical hole 8d. A check valve 25 that allows only the flow of liquid is provided. The check valve 25 is seated on the pipe 25a mounted in the vertical hole 8d, a cup-shaped spring receiver 25b fitted to the pipe 25a, and an end of the pipe 25a and accommodated in the spring receiver 25b. A disc-like valve body 25c, and a spring 25d interposed between the top of the spring receiver 25b and the valve body 25c. The spring receiver 25b is provided with a notch, and when the valve body 25c is separated from the pipe 25a, the check valve 25 is opened to allow the flow of liquid from the vertical hole 8d side toward the pressure side chamber R2. On the other hand, for the opposite liquid flow, the valve body 25c contacts the lower end of the pipe 25a in FIG. 1 and the check valve 25 closes to block the liquid flow. Thus, the check valve 25 is assembled and accommodated in the vertical hole 8d, and is fixed to the vertical hole 8d by a disc spring fitted near the outlet of the vertical hole 8d. Therefore, the extension side discharge passage Ee blocks the flow of liquid from the pressure side chamber R2 toward the adjustment passage Pc, and allows only the flow of liquid from the adjustment passage Pc toward the pressure side chamber R2.
　ロッド部材１０は、筒状であって、図１中下端の内周が拡径されていて電磁弁収容筒９の連結部９ｂの挿入を許容し、この連結部９ｂの螺着を可能とする螺子部（符示せず）を備えている。このように、ロッド部材１０、電磁弁収容筒９及びピストンホルダ８を一体化すると、これらでピストンロッド７が形成される。 The rod member 10 has a cylindrical shape, and the inner circumference at the lower end in FIG. 1 has an enlarged diameter, allows insertion of the connecting portion 9b of the solenoid valve housing cylinder 9, and enables the connecting portion 9b to be screwed. A screw portion (not shown) is provided. Thus, when the rod member 10, the solenoid valve housing cylinder 9, and the piston holder 8 are integrated, the piston rod 7 is formed by these.
　なお、ロッド部材１０内及び電磁弁収容筒９における連結部９ｂ内には、後述するソレノイドへ電力供給するハーネスＨが挿通されており、ハーネスＨの上端は、図示はしないがロッド部材１０の上端から外方へ伸びていて電源に接続される。 A harness H for supplying power to a solenoid, which will be described later, is inserted into the rod member 10 and the connecting portion 9b of the solenoid valve housing cylinder 9, and the upper end of the harness H is not shown, but the upper end of the rod member 10 is not shown. Is connected to the power supply.
　ピストンホルダ８に設けた保持軸８ａの外周には、図３に示すように、環状のピストン２とともに、複数の環状板を積層して構成されたシム６１と、同じくシム６１の外周に摺動自在に装着される圧側環状プレート６２、環状であって外径がシム６１より大径な圧側ストッパ６３と、圧側チャンバ部材１１とが重ねられて組付けられる。また、ピストン２に重ねられて、シム６１の外周に摺動自在に装着される環状の圧側リーフバルブＶｐが設けられており、圧側リーフバルブＶｐは、シム６１を介してピストンホルダ８の保持軸８ａの外周に取付けられている。圧側チャンバ部材１１には、前記圧側環状プレート６２に当接する圧側スプールＳｐが摺動自在に装着されており、圧側スプールＳｐは、軸方向移動可能とされて圧側チャンバ部材１１と共に圧側背圧室Ｃｐを形成している。 As shown in FIG. 3, the outer periphery of the holding shaft 8 a provided in the piston holder 8 slides on the outer periphery of the shim 61 and the shim 61 formed by laminating a plurality of annular plates together with the annular piston 2. A pressure-side annular plate 62 that is freely mounted, a pressure-side stopper 63 that is annular and has an outer diameter larger than that of the shim 61, and the pressure-side chamber member 11 are assembled in an overlapping manner. Further, an annular pressure side leaf valve Vp that is slidably mounted on the outer periphery of the shim 61 is provided on the piston 2, and the pressure side leaf valve Vp is connected to the holding shaft of the piston holder 8 via the shim 61. It is attached to the outer periphery of 8a. The pressure side chamber member 11 is slidably mounted with a pressure side spool Sp that is in contact with the pressure side annular plate 62, and the pressure side spool Sp is movable in the axial direction so as to move together with the pressure side chamber member 11. Is forming.
　また、ピストン２の図３中下方には、複数の環状板を積層して構成された軸部材としてのシム６５と、同じくシム６５の外周に摺動自在に装着される伸側環状プレート６６、環状であって外径がシム６５より大径な伸側ストッパ６７、伸側チャンバ部材１２とが重ねて組付けられる。また、ピストン２に重ねられて、シム６５の外周に摺動自在に装着される環状の伸側リーフバルブＶｅが設けられており、伸側リーフバルブＶｅは、シム６５を介してピストンホルダ８の保持軸８ａの外周に取付けられている。伸側チャンバ部材１２には、前記伸側環状プレート６６に当接する伸側スプールＳｅが摺動自在に装着されており、伸側スプールＳｅは、軸方向移動が可能とされ、伸側チャンバ部材１２と共に伸側背圧室Ｃｅを形成している。なお、伸側リーフバルブＶｅの外径は、圧側リーフバルブＶｐの外径より小径となっている。 Further, below the piston 2 in FIG. 3, a shim 65 as a shaft member configured by laminating a plurality of annular plates, and an extended-side annular plate 66 that is slidably mounted on the outer periphery of the shim 65, An extension side stopper 67 and an extension side chamber member 12 which are annular and have an outer diameter larger than that of the shim 65 are assembled in an overlapping manner. Further, an annular extension side leaf valve Ve that is slidably mounted on the outer periphery of the shim 65 is provided on the piston 2, and the extension side leaf valve Ve is connected to the piston holder 8 via the shim 65. It is attached to the outer periphery of the holding shaft 8a. An extension side spool Se that contacts the extension side annular plate 66 is slidably attached to the extension side chamber member 12, and the extension side spool Se can be moved in the axial direction. In addition, an extension side back pressure chamber Ce is formed. The outer diameter of the extension side leaf valve Ve is smaller than the outer diameter of the compression side leaf valve Vp.
　そして、前述した保持軸８ａの外周に装着される各部品は、保持軸８ａの先端に形成された螺子部８ｆに螺着される伸側チャンバ部材１２によって固定される。 Then, each component mounted on the outer periphery of the holding shaft 8a described above is fixed by the extension-side chamber member 12 screwed into a screw portion 8f formed at the tip of the holding shaft 8a.
　ピストン２は、環状であってピストンホルダ８の保持軸８ａの外周に装着されており、伸側室Ｒ１と圧側室Ｒ２とを連通する伸側通路３と圧側通路４とが形成されている。また、図３においてピストン２の上端には、圧側通路４に連通される環状窓２ａと、環状窓２ａの外周側に設けられて圧側通路４を囲む環状の圧側弁座２ｂと、環状窓２ａの内周に設けた内周シート部２ｃとが設けられている。他方、ピストン２の下端には、伸側通路３に連通される環状窓２ｄと、環状窓２ｄの外周側に設けられて伸側通路３を囲む環状の伸側弁座２ｅと、環状窓２ｄの内周に設けた内周シート部２ｆとが設けられている。 The piston 2 is annular and is mounted on the outer periphery of the holding shaft 8a of the piston holder 8, and an extension side passage 3 and a pressure side passage 4 that connect the extension side chamber R1 and the pressure side chamber R2 are formed. 3, at the upper end of the piston 2, there is an annular window 2a communicating with the pressure side passage 4, an annular pressure side valve seat 2b provided on the outer peripheral side of the annular window 2a and surrounding the pressure side passage 4, and an annular window 2a. The inner periphery sheet | seat part 2c provided in the inner periphery is provided. On the other hand, at the lower end of the piston 2, an annular window 2d communicated with the extension side passage 3, an annular extension side valve seat 2e provided on the outer peripheral side of the annular window 2d and surrounding the extension side passage 3, and an annular window 2d. The inner periphery sheet | seat part 2f provided in the inner periphery is provided.
　伸側リーフバルブＶｅは、図３に示すように、ピストンホルダ８の保持軸８ａの挿通を許容するため環状とされており、この例では、一枚の環状板で構成されているが、複数枚の環状板を積層して構成されてもよい。そして、このように構成された伸側リーフバルブＶｅは、ピストン２の図３中下方に重ねられていて、伸側弁座２ｅおよび内周シート部２ｆに離着座可能とされている。 As shown in FIG. 3, the extension-side leaf valve Ve is annular in order to allow insertion of the holding shaft 8 a of the piston holder 8. In this example, the extension-side leaf valve Ve is composed of a single annular plate. It may be configured by laminating a single annular plate. The extension side leaf valve Ve configured as described above is overlapped below the piston 2 in FIG. 3 and can be attached to and detached from the extension side valve seat 2e and the inner peripheral seat portion 2f.
　また、伸側リーフバルブＶｅは、その外周に伸側弁座２ｅへ着座した際にオリフィスとして機能する切欠Ｏｅを備えており、シム６５の外周に摺動自在に装着されている。シム６５の外周には、伸側リーフバルブＶｅに重ねられる伸側環状プレート６６が摺動自在に装着されている。なお、本実施の形態では、伸側環状プレート６６の反伸側リーフバルブ側に伸側環状プレート６６よりも外径が小径な環状の補助バルブ７１が重ねられており、この補助バルブ７１もまたシム６５の外周に摺動自在に装着されている。伸側リーフバルブＶｅ、伸側環状プレート６６および補助バルブ７１を積層した際の軸方向長さは、シム６５の軸方向長さよりも短くなるようにしてある。さらに、シム６５の図３中下方には、環状であって外径が補助バルブ７１および伸側環状プレート６６の内径よりも大径に設定される伸側ストッパ６７が設けられており、この伸側ストッパ６７の下方に伸側チャンバ部材１２が重ねられる。よって、伸側リーフバルブＶｅ、伸側環状プレート６６および補助バルブ７１は、シム６５によってガイドされてピストン２と伸側ストッパ６７との間で軸方向となる図３中上下方向へ移動できるようになっている。 The extension side leaf valve Ve is provided with a notch Oe that functions as an orifice when seated on the extension side valve seat 2e on the outer periphery thereof, and is slidably mounted on the outer periphery of the shim 65. On the outer periphery of the shim 65, an expansion side annular plate 66 that is superimposed on the expansion side leaf valve Ve is slidably mounted. In this embodiment, an annular auxiliary valve 71 having an outer diameter smaller than that of the expansion side annular plate 66 is stacked on the side of the expansion side annular plate 66 opposite to the leaf valve side. The outer periphery of the shim 65 is slidably mounted. The axial length when the extension-side leaf valve Ve, the extension-side annular plate 66 and the auxiliary valve 71 are stacked is made shorter than the axial length of the shim 65. Further, an extension side stopper 67 is provided below the shim 65 in FIG. 3 and has an annular shape whose outer diameter is set larger than the inner diameters of the auxiliary valve 71 and the extension side annular plate 66. The extension side chamber member 12 is stacked below the side stopper 67. Accordingly, the extension side leaf valve Ve, the extension side annular plate 66 and the auxiliary valve 71 are guided by the shim 65 so as to be movable in the vertical direction in FIG. 3 which is the axial direction between the piston 2 and the extension side stopper 67. It has become.
　そして、伸側リーフバルブＶｅは、伸側通路３側から圧力によって押圧されると、外周が伸側環状プレート６６とともに撓むとともに、伸側環状プレート６６および補助バルブ７１とともに全体がピストン２から離間して後退できる。伸側リーフバルブＶｅ、伸側環状プレート６６および補助バルブ７１のピストン２からの後退量は、シム６５の軸方向長さによって設定される。この場合、シム６５が複数枚の環状板で構成されるので、環状板の積層枚数で調節可能であるが、シム６５を単一の環状板で構成してもよい。 When the extension-side leaf valve Ve is pressed by pressure from the extension-side passage 3 side, the outer periphery bends together with the extension-side annular plate 66, and the extension-side leaf plate Ve and the auxiliary valve 71 as a whole are separated from the piston 2. Can retreat. The retraction amounts of the extension side leaf valve Ve, the extension side annular plate 66 and the auxiliary valve 71 from the piston 2 are set by the axial length of the shim 65. In this case, since the shim 65 is constituted by a plurality of annular plates, the shim 65 can be adjusted by the number of laminated annular plates, but the shim 65 may be constituted by a single annular plate.
　伸側環状プレート６６は、伸側リーフバルブＶｅよりも撓み剛性が高くなっている。そのため、伸側環状プレート６６の軸方向長さ（厚み）を伸側リーフバルブＶｅの軸方向長さ（厚み）より長くしてあるが、軸方向長さによって剛性を強くするだけでなく、伸側リーフバルブＶｅよりも高剛性の材料で伸側環状プレート６６を形成するようにしてもよい。 The expansion side annular plate 66 is bent and has higher rigidity than the expansion side leaf valve Ve. For this reason, the axial length (thickness) of the expansion side annular plate 66 is longer than the axial length (thickness) of the expansion side leaf valve Ve. The expansion-side annular plate 66 may be formed of a material having higher rigidity than the side leaf valve Ve.
　ここで、伸側環状プレート６６の内径は、ピストン２に設けた内周シート部２ｆの外径よりも小径に設定されている。伸側環状プレート６６の外径は、伸側弁座２ｅの内径よりも大径に設定されている。ここで、伸側背圧室Ｃｅは、内部に導入される圧力で伸側スプールＳｅを伸側環状プレート６６へ向けて附勢している。よって、伸側環状プレート６６に重ねる伸側リーフバルブＶｅには、伸側スプールＳｅから受ける附勢力と伸側背圧室Ｃｅの圧力によってピストン２側へ向けて附勢される。伸側環状プレート６６が背面側から伸側背圧室Ｃｅ内の圧力と伸側スプールＳｅによって押圧されて、伸側リーフバルブＶｅが伸側弁座２ｅと内周シート部２ｆとに着座すると、伸側環状プレート６６が内周シート部２ｆと伸側弁座２ｅとで支持される格好になる。そのため、伸側背圧室Ｃｅ内の圧力と伸側スプールＳｅによる附勢力を伸側環状プレート６６で受け止めるようになり、伸側リーフバルブＶｅの変形が抑制され、伸側リーフバルブＶｅに過負荷がかからないようになっている。また、補助バルブ７１は、伸側リーフバルブＶｅおよび伸側環状プレート６６よりも外径が小径に設定されている。そのため、伸側リーフバルブＶｅおよび伸側環状プレート６６が伸側通路３の圧力で撓む場合に、補助バルブ７１よりも外周側の方が撓みやすくなっていて、補助バルブ７１を用いて伸側減衰力の減衰特性をチューニングできる。緩衝器Ｄに発生させる減衰特性により補助バルブ７１が不要であれば省略できる。反対に、補助バルブ７１を複数枚積層してもよい。 Here, the inner diameter of the expansion side annular plate 66 is set to be smaller than the outer diameter of the inner peripheral sheet portion 2f provided in the piston 2. The outer diameter of the expansion side annular plate 66 is set to be larger than the inner diameter of the expansion side valve seat 2e. Here, the extension-side back pressure chamber Ce urges the extension-side spool Se toward the extension-side annular plate 66 with the pressure introduced inside. Therefore, the extension side leaf valve Ve stacked on the extension side annular plate 66 is urged toward the piston 2 by the urging force received from the extension side spool Se and the pressure of the extension side back pressure chamber Ce. When the expansion side annular plate 66 is pressed from the back side by the pressure in the expansion side back pressure chamber Ce and the expansion side spool Se, and the expansion side leaf valve Ve is seated on the expansion side valve seat 2e and the inner peripheral seat portion 2f, The extension side annular plate 66 is supported by the inner peripheral seat portion 2f and the extension side valve seat 2e. Therefore, the pressure in the extension side back pressure chamber Ce and the urging force of the extension side spool Se are received by the extension side annular plate 66, and deformation of the extension side leaf valve Ve is suppressed, and the extension side leaf valve Ve is overloaded. It is not to take. The auxiliary valve 71 has an outer diameter smaller than that of the extension side leaf valve Ve and the extension side annular plate 66. Therefore, when the extension side leaf valve Ve and the extension side annular plate 66 are bent by the pressure of the extension side passage 3, the outer peripheral side is more easily bent than the auxiliary valve 71. The damping characteristic of damping force can be tuned. If the auxiliary valve 71 is unnecessary due to the damping characteristic generated in the shock absorber D, it can be omitted. Conversely, a plurality of auxiliary valves 71 may be stacked.
　続いて、伸側チャンバ部材１２は、伸側リーフバルブＶｅの反ピストン側に配置され、ピストンホルダ８における保持軸８ａの先端外周に螺着される筒状のスペーサ１２１と、スペーサ１２１の外周に嵌合されて伸側スプールＳｅが摺接する摺接筒１２２とを備えている。スペーサ１２１は、保持軸８ａの螺子部８ｆに螺着される筒部１２１ａと、筒部１２１ａの図３中下端外周に設けたフランジ１２１ｂと、筒部１２１ａの内周に設けられた環状溝１２１ｃと、環状溝１２１ｃから開口して筒部１２１ａを貫通する圧側抵抗要素としての圧側パイロットオリフィスＰｐとを備えている。また、摺接筒１２２は、内周に伸側スプールＳｅが摺接する筒部１２２ａと、筒部１２２ａの図３中下端内周に突出するフランジ１２２ｂとを備えている。 Subsequently, the extension-side chamber member 12 is disposed on the opposite side of the extension-side leaf valve Ve from the piston, and has a cylindrical spacer 121 that is screwed to the outer periphery of the holding shaft 8a of the piston holder 8, and an outer periphery of the spacer 121. And a sliding contact cylinder 122 that is fitted and in sliding contact with the expansion side spool Se. The spacer 121 includes a cylindrical portion 121a that is screwed to the screw portion 8f of the holding shaft 8a, a flange 121b that is provided on the outer periphery of the lower end in FIG. 3 of the cylindrical portion 121a, and an annular groove 121c that is provided on the inner periphery of the cylindrical portion 121a. And a pressure side pilot orifice Pp as a pressure side resistance element that opens from the annular groove 121c and penetrates the cylindrical portion 121a. Further, the sliding contact cylinder 122 includes a cylindrical portion 122a in which the extension side spool Se is in sliding contact with the inner periphery, and a flange 122b that protrudes to the inner periphery at the lower end in FIG. 3 of the cylindrical portion 122a.
　摺接筒１２２のフランジ１２２ｂの内周には、スペーサ１２１の筒部１２１ａが嵌合されて、フランジ１２１ｂ，１２２ｂ同士を当接させるとスペーサ１２１と摺接筒１２２が一体となって環状凹部が形成されて、この環状凹部で伸側背圧室Ｃｅが形成される。なお、本例では、加工を容易とするために伸側チャンバ部材１２をスペーサ１２１と摺接筒１２２とで構成しているが、一部品で構成してもよい。 The cylindrical portion 121a of the spacer 121 is fitted to the inner periphery of the flange 122b of the sliding contact tube 122. When the flanges 121b and 122b are brought into contact with each other, the spacer 121 and the sliding contact tube 122 are integrated to form an annular recess. Thus, the extension-side back pressure chamber Ce is formed by the annular recess. In this example, the extension side chamber member 12 is constituted by the spacer 121 and the sliding contact cylinder 122 in order to facilitate processing, but may be constituted by one part.
　そして、伸側チャンバ部材１２を保持軸８ａに組み付けると、スペーサ１２１の内周の環状溝１２１ｃが保持軸８ａに設けた溝８ｈに対向して、伸側背圧室Ｃｅが圧側パイロットオリフィスＰｐを通じて溝８ｈに連通される。 When the extension side chamber member 12 is assembled to the holding shaft 8a, the annular groove 121c on the inner periphery of the spacer 121 faces the groove 8h provided on the holding shaft 8a, and the extension side back pressure chamber Ce passes through the pressure side pilot orifice Pp. It communicates with the groove 8h.
　なお、伸側チャンバ部材１２におけるスペーサ１２１とシム６５との間には、伸側ストッパ６７を介装してあるが、伸側ストッパ６７を廃止してスペーサ１２１をストッパとして機能させて伸側環状プレート６６の移動下限を規制するようにしてもよい。 An extension side stopper 67 is interposed between the spacer 121 and the shim 65 in the extension side chamber member 12, but the extension side stopper 67 is abolished so that the spacer 121 functions as a stopper. The lower limit of movement of the plate 66 may be restricted.
　摺接筒１２２内には、伸側スプールＳｅが収容される。伸側スプールＳｅは、外周を摺接筒１２２における筒部１２２ａの内周に摺接させており、当該摺接筒１２２内で軸方向へ移動できるようになっている。伸側スプールＳｅは、環状のスプール本体１３と、スプール本体１３の図３中上端内周から立ち上がる環状突起１４とを備えている。この環状突起１４の内径は、伸側環状プレート６６の外径よりも小径に設定されており、環状突起１４が伸側環状プレート６６の背面となる図３中下面に当接できるようになっている。 The extension side spool Se is accommodated in the sliding tube 122. The extension-side spool Se is in sliding contact with the inner periphery of the cylindrical portion 122 a of the sliding contact cylinder 122, and can move in the axial direction within the sliding contact cylinder 122. The extension-side spool Se includes an annular spool body 13 and an annular protrusion 14 that rises from the inner periphery of the upper end of the spool body 13 in FIG. The inner diameter of the annular protrusion 14 is set to be smaller than the outer diameter of the extended-side annular plate 66 so that the annular protrusion 14 can come into contact with the lower surface in FIG. Yes.
　なお、スプール本体１３の内径は、スペーサ１２１の筒部１２１ａの外径より大きくしているが、前記内径を筒部１２１ａの外周に摺接する径に設定して、伸側背圧室Ｃｅを伸側スプールＳｅで封じてもよい。 The inner diameter of the spool body 13 is larger than the outer diameter of the cylindrical portion 121a of the spacer 121, but the inner diameter is set to a diameter that is in sliding contact with the outer periphery of the cylindrical portion 121a to extend the extension-side back pressure chamber Ce. You may seal with the side spool Se.
　さらに、伸側チャンバ部材１２の摺接筒１２２には、フランジ１２２ｂを貫通して伸側背圧室Ｃｅと圧側室Ｒ２とを連通する圧側圧力導入通路Ｉｐが設けられている。摺接筒１２２のフランジ１２２ｂの図３中上端には、環状弁体１５が重ねられており、この環状弁体１５と伸側スプールＳｅにおけるスプール本体１３との間に介装されたばね１６によって環状弁体１５がフランジ１２２ｂへ押しつけられている。また、圧側圧力導入通路Ｉｐは、通過液体の流れに対して抵抗を生じさせないように配慮されている。 Further, the sliding contact cylinder 122 of the extension side chamber member 12 is provided with a pressure side pressure introduction passage Ip that passes through the flange 122b and communicates the extension side back pressure chamber Ce and the pressure side chamber R2. An annular valve body 15 is superimposed on the upper end of the flange 122b of the sliding contact cylinder 122 in FIG. 3, and is annularly formed by a spring 16 interposed between the annular valve body 15 and the spool body 13 of the extension side spool Se. The valve body 15 is pressed against the flange 122b. Further, the pressure side pressure introduction passage Ip is considered so as not to cause resistance to the flow of the passing liquid.
　この環状弁体１５は、緩衝器Ｄの収縮作動時において、圧側室Ｒ２が圧縮されて圧力が高まると、この圧力によって押圧されてフランジ１２２ｂから離座して圧側圧力導入通路Ｉｐを開放する。また、伸側背圧室Ｃｅ内の圧力が圧側室Ｒ２より高くなる緩衝器Ｄの伸長作動時にはフランジ１２２ｂに押しつけられて圧側圧力導入通路Ｉｐを閉塞し、圧側室Ｒ２からの液体の流れのみを許容する。このように、環状弁体１５とばね１６は、圧側逆止弁Ｔｐを構成しており、圧側圧力導入通路Ｉｐを圧側室Ｒ２から伸側背圧室Ｃｅへ向かう液体の流れのみを許容する一方通行の通路に設定している。 When the pressure side chamber R2 is compressed and the pressure is increased during the contraction operation of the shock absorber D, the annular valve body 15 is pressed by this pressure and is separated from the flange 122b to open the pressure side pressure introduction passage Ip. Further, when the shock absorber D is extended so that the pressure in the extension side back pressure chamber Ce becomes higher than the pressure side chamber R2, it is pressed against the flange 122b to close the pressure side pressure introduction passage Ip, and only the liquid flow from the pressure side chamber R2 is allowed to flow. Allow. As described above, the annular valve body 15 and the spring 16 constitute the pressure-side check valve Tp, and only allow the flow of liquid from the pressure-side chamber R2 toward the extension-side back pressure chamber Ce through the pressure-side pressure introduction passage Ip. It is set as a passage for traffic.
　ばね１６は、環状弁体１５をフランジ１２２ｂに押し付ける役割を担って、環状弁体１５とともに圧側逆止弁Ｔｐを構成するとともに、伸側スプールＳｅを伸側リーフバルブＶｅへ向けて附勢する役割をも担っている。よって、伸側リーフバルブＶｅが撓んで伸側スプールＳｅがピストン２から離間する方向へ押し下げられてから伸側リーフバルブＶｅの撓みが解消すると、ばね１６のばね力で伸側スプールＳｅが速やかに元の位置（図３に示す位置）へ戻る。伸側スプールＳｅの附勢を別途のばねで附勢できるが、圧側逆止弁Ｔｐとばね１６を共用でき部品点数を削減できるとともに構造が簡単となる利点がある。なお、伸側スプールＳｅの外径は、環状突起１４の内径よりも大径に設定されていて、環状突起１４が伸側環状プレート６６に当接するようになっているので、伸側スプールＳｅは伸側背圧室Ｃｅの圧力によって常に伸側リーフバルブＶｅへ向けて附勢される。 The spring 16 plays a role of pressing the annular valve body 15 against the flange 122b, constitutes a compression-side check valve Tp together with the annular valve body 15, and serves to urge the extension-side spool Se toward the extension-side leaf valve Ve. Is also responsible. Therefore, when the extension side leaf valve Ve is bent and the extension side spool Se is pushed down in the direction away from the piston 2 and then the extension side leaf valve Ve is flexed, the extension side spool Se is quickly moved by the spring force of the spring 16. Return to the original position (position shown in FIG. 3). Although the energization of the extension side spool Se can be energized by a separate spring, there is an advantage that the compression side check valve Tp and the spring 16 can be shared, the number of parts can be reduced, and the structure can be simplified. The outer diameter of the extension side spool Se is set to be larger than the inner diameter of the annular protrusion 14, and the annular protrusion 14 comes into contact with the extension side annular plate 66. The pressure in the extension side back pressure chamber Ce is always urged toward the extension side leaf valve Ve.
　ピストン２の上方に重ねられる圧側リーフバルブＶｐは、図３に示すように、伸側リーフバルブＶｅ同様に、ピストンホルダ８の保持軸８ａの挿通を許容するため環状とされており、この例では、一枚の環状板で構成されているが、複数枚の環状板を積層して構成されてもよい。そして、このように構成された圧側リーフバルブＶｐは、ピストン２の図３中上方に重ねられていて、圧側弁座２ｂおよび内周シート部２ｃに離着座可能とされている。 As shown in FIG. 3, the pressure side leaf valve Vp overlaid on the piston 2 has an annular shape to allow the holding shaft 8a of the piston holder 8 to be inserted, as in the extension side leaf valve Ve. Although it is constituted by one annular plate, it may be constituted by laminating a plurality of annular plates. And the pressure side leaf valve Vp comprised in this way is piled up the upper direction in FIG. 3 of the piston 2, and can be attached / detached to the pressure side valve seat 2b and the inner peripheral seat part 2c.
　また、圧側リーフバルブＶｐは、その外周に圧側弁座２ｂへ着座した際にオリフィスとして機能する切欠Ｏｐを備えており、シム６１の外周に摺動自在に装着されている。シム６１の外周には、圧側リーフバルブＶｐに重ねられる圧側環状プレート６２が摺動自在に装着されている。なお、本実施の形態では、圧側環状プレート６２の反圧側リーフバルブ側に圧側環状プレート６２よりも外径が小径な環状の補助バルブ８１が重ねられており、この補助バルブ８１もまたシム６１の外周に摺動自在に装着されている。圧側リーフバルブＶｐ、圧側環状プレート６２および補助バルブ８１を積層した際の軸方向長さは、シム６１の軸方向長さよりも短くなるようにしてある。さらに、シム６１の図３中上方には、環状であって外径が補助バルブ８１および圧側環状プレート６２の内径よりも大径に設定される圧側ストッパ６３が設けられており、この圧側ストッパ６３の上方に圧側チャンバ部材１１が重ねられる。よって、圧側リーフバルブＶｐ、圧側環状プレート６２および補助バルブ８１は、シム６１によってガイドされてピストン２と圧側ストッパ６３との間で軸方向となる図３中上下方向へ移動できるようになっている。 The pressure-side leaf valve Vp is provided with a notch Op that functions as an orifice when seated on the pressure-side valve seat 2b on the outer periphery thereof, and is slidably mounted on the outer periphery of the shim 61. On the outer periphery of the shim 61, a pressure side annular plate 62 that is superimposed on the pressure side leaf valve Vp is slidably mounted. In the present embodiment, an annular auxiliary valve 81 having an outer diameter smaller than that of the pressure side annular plate 62 is stacked on the pressure side leaf valve side of the pressure side annular plate 62, and this auxiliary valve 81 is also connected to the shim 61. It is slidably mounted on the outer periphery. The axial length when the pressure side leaf valve Vp, the pressure side annular plate 62 and the auxiliary valve 81 are stacked is set to be shorter than the axial length of the shim 61. Further, a pressure side stopper 63 is provided above the shim 61 in FIG. 3 and has an annular shape whose outer diameter is set larger than the inner diameter of the auxiliary valve 81 and the pressure side annular plate 62. The compression side chamber member 11 is overlaid on the upper side. Therefore, the pressure-side leaf valve Vp, the pressure-side annular plate 62, and the auxiliary valve 81 are guided by the shim 61 and can move up and down in FIG. 3, which is the axial direction between the piston 2 and the pressure-side stopper 63. .
　そして、圧側リーフバルブＶｐは、圧側通路４側から圧力によって押圧されると、外周が圧側環状プレート６２とともに撓むとともに、圧側環状プレート６２および補助バルブ８１とともに全体がピストン２から離間して後退できる。圧側リーフバルブＶｐ、圧側環状プレート６２および補助バルブ８１のピストン２からの後退量は、シム６１の軸方向長さによって設定される。この場合、シム６１が複数枚の環状板で構成されるので、環状板の積層枚数で調節可能であるが、シム６１を単一の環状板で構成してもよい。 When the pressure-side leaf valve Vp is pressed by pressure from the pressure-side passage 4 side, the outer periphery thereof bends together with the pressure-side annular plate 62, and the pressure-side leaf plate Vp and the auxiliary valve 81 can be moved away from the piston 2 as a whole. The retraction amounts of the pressure side leaf valve Vp, the pressure side annular plate 62 and the auxiliary valve 81 from the piston 2 are set by the length of the shim 61 in the axial direction. In this case, since the shim 61 is constituted by a plurality of annular plates, the shim 61 can be adjusted by the number of laminated annular plates, but the shim 61 may be constituted by a single annular plate.
　圧側環状プレート６２は、圧側リーフバルブＶｐよりも撓み剛性が高くなっている。そのため、圧側環状プレート６２の軸方向長さ（厚み）を圧側リーフバルブＶｐの軸方向長さ（厚み）より長くしてあるが、軸方向長さによって剛性を強くするだけでなく、圧側リーフバルブＶｐよりも高剛性の材料で圧側環状プレート６２を形成するようにしてもよい。 The pressure side annular plate 62 is bent and has higher rigidity than the pressure side leaf valve Vp. For this reason, the axial length (thickness) of the compression-side annular plate 62 is longer than the axial length (thickness) of the compression-side leaf valve Vp, but not only the rigidity is increased by the axial length but also the compression-side leaf valve. The compression side annular plate 62 may be formed of a material having higher rigidity than Vp.
　ここで、圧側環状プレート６２の内径は、ピストン２に設けた内周シート部２ｃの外径よりも小径に設定されている。圧側環状プレート６２の外径は、圧側弁座２ｂの内径よりも大径に設定されている。ここで、圧側背圧室Ｃｐは、内部に導入される圧力で圧側スプールＳｐを圧側環状プレート６２へ向けて附勢している。よって、圧側環状プレート６２に重なる圧側リーフバルブＶｐには、圧側スプールＳｐから受ける附勢力と圧側背圧室Ｃｐの圧力によってピストン２側へ向けて附勢される。圧側環状プレート６２が背面側から圧側背圧室Ｃｐ内の圧力と圧側スプールＳｐによって押圧されて、圧側リーフバルブＶｐが圧側弁座２ｂと内周シート部２ｃとに着座すると、圧側環状プレート６２が内周シート部２ｃと圧側弁座２ｂとで支持される格好になる。そのため、圧側背圧室Ｃｐ内の圧力と圧側スプールＳｐによる附勢力を圧側環状プレート６２で受け止めるようになり、圧側リーフバルブＶｐの変形が抑制され、圧側リーフバルブＶｐに過負荷がかからないようになっている。また、補助バルブ８１は、圧側リーフバルブＶｐおよび圧側環状プレート６２よりも外径が小径に設定されている。そのため、圧側リーフバルブＶｐおよび圧側環状プレート６２が圧側通路４の圧力で撓む場合に、補助バルブ８１よりも外周側の方が撓みやすくなっていて、補助バルブ８１を用いて圧側減衰力の減衰特性をチューニングできる。緩衝器Ｄに発生させる減衰特性により補助バルブ８１が不要であれば省略できる。反対に、補助バルブ８１を複数枚積層してもよい。 Here, the inner diameter of the compression side annular plate 62 is set to be smaller than the outer diameter of the inner peripheral sheet portion 2c provided in the piston 2. The outer diameter of the pressure side annular plate 62 is set to be larger than the inner diameter of the pressure side valve seat 2b. Here, the pressure-side back pressure chamber Cp urges the pressure-side spool Sp toward the pressure-side annular plate 62 with the pressure introduced inside. Therefore, the pressure side leaf valve Vp overlapping the pressure side annular plate 62 is urged toward the piston 2 by the urging force received from the pressure side spool Sp and the pressure in the pressure side back pressure chamber Cp. When the pressure side annular plate 62 is pressed from the back side by the pressure in the pressure side back pressure chamber Cp and the pressure side spool Sp, and the pressure side leaf valve Vp is seated on the pressure side valve seat 2b and the inner peripheral seat portion 2c, the pressure side annular plate 62 is The inner circumferential seat portion 2c and the pressure side valve seat 2b are supported. Therefore, the pressure in the pressure side back pressure chamber Cp and the urging force by the pressure side spool Sp are received by the pressure side annular plate 62, the deformation of the pressure side leaf valve Vp is suppressed, and the pressure side leaf valve Vp is not overloaded. ing. The auxiliary valve 81 has an outer diameter smaller than that of the pressure side leaf valve Vp and the pressure side annular plate 62. Therefore, when the pressure side leaf valve Vp and the pressure side annular plate 62 are bent by the pressure of the pressure side passage 4, the outer peripheral side is more easily bent than the auxiliary valve 81, and the auxiliary side valve 81 is used to attenuate the pressure side damping force. You can tune the characteristics. If the auxiliary valve 81 is unnecessary due to the damping characteristic generated in the shock absorber D, it can be omitted. Conversely, a plurality of auxiliary valves 81 may be stacked.
　続いて、圧側チャンバ部材１１は、圧側リーフバルブＶｐの反ピストン側に配置され、ピストンホルダ８における保持軸８ａの外周に嵌合される筒状のスペーサ１１１と、スペーサ１１１の外周に嵌合されて圧側スプールＳｐが摺接する摺接筒１１２とを備えている。スペーサ１１１は、保持軸８ａの外周に装着されており、図３中上端外周全周に亘って設けられた凹部１１１ａと、内周に設けられた環状溝１１１ｂと、環状溝１１１ｂから開口して外周側へ貫通する伸側抵抗要素としての伸側パイロットオリフィスＰｅとを備えている。また、摺接筒１１２は、内周に圧側スプールＳｐが摺接する筒部１１２ａと、筒部１１２ａの図３中上端内周に突出するフランジ１１２ｂとを備えている。 Subsequently, the pressure side chamber member 11 is disposed on the side opposite to the piston of the pressure side leaf valve Vp, and is fitted to the outer periphery of the spacer 111 and the cylindrical spacer 111 fitted to the outer periphery of the holding shaft 8 a in the piston holder 8. And a sliding cylinder 112 with which the compression side spool Sp slides. The spacer 111 is mounted on the outer periphery of the holding shaft 8a, and opens from the recess 111a provided on the entire outer periphery of the upper end in FIG. 3, the annular groove 111b provided on the inner periphery, and the annular groove 111b. An extension side pilot orifice Pe as an extension side resistance element penetrating to the outer peripheral side is provided. Further, the slidable contact cylinder 112 includes a cylinder portion 112a in which the compression side spool Sp is slidably contacted on the inner periphery, and a flange 112b protruding from the upper end inner periphery in FIG. 3 of the cylinder portion 112a.
　摺接筒１１２のフランジ１１２ｂの内周をスペーサ１１１の凹部１１１ａに嵌合すると、スペーサ１１１と摺接筒１１２が一体となって環状凹部が形成されて、この環状凹部で圧側背圧室Ｃｐが形成される。なお、本例では、加工を容易とするために圧側チャンバ部材１１をスペーサ１１１と摺接筒１１２とで構成しているが、一部品で構成してもよい。 When the inner periphery of the flange 112b of the sliding contact cylinder 112 is fitted into the recess 111a of the spacer 111, the spacer 111 and the sliding contact cylinder 112 are integrated to form an annular recess, and the pressure side back pressure chamber Cp is formed in the annular recess. It is formed. In this example, the pressure side chamber member 11 is composed of the spacer 111 and the sliding contact cylinder 112 in order to facilitate processing, but it may be composed of one part.
　そして、圧側チャンバ部材１１を保持軸８ａに組み付けると、スペーサ１１１の内周の環状溝１１１ｂが保持軸８ａに設けた溝８ｈに対向して、圧側背圧室Ｃｐが伸側パイロットオリフィスＰｅを通じて溝８ｈに連通される。圧側チャンバ部材１１は、図３中上端がピストンホルダ８のフランジ８ｂに当接して密着している。そして、溝８ｈは、保持軸８ａに装着されるピストン２、シム６１，６５、伸側ストッパ６７および圧側ストッパ６３、伸側チャンバ部材１２および圧側チャンバ部材１１によって、伸側室Ｒ１および圧側室Ｒ２との連通が絶たれている。また、スペーサ１１１の図３中上端内周の径は、拡径されていて、保持軸８ａとの間に環状の空隙が形成されており、溝８ｈは、空隙を介してピストンホルダ８に設けたポート８ｅに通じている。よって、溝８ｈは、ポート８ｅを介して収容部Ｌに通じていて、調節通路Ｐｃに接続されるとともに、圧側パイロットオリフィスＰｐを通じて伸側背圧室Ｃｅと伸側パイロットオリフィスＰｅを通じて圧側背圧室Ｃｐに接続されている。このように、溝８ｈは、圧側抵抗要素を介して伸側背圧室Ｃｅに連通されるともに伸側抵抗要素を介して圧側背圧室Ｃｐに連通される連通路を形成している。 When the pressure-side chamber member 11 is assembled to the holding shaft 8a, the annular groove 111b on the inner periphery of the spacer 111 faces the groove 8h provided on the holding shaft 8a, and the pressure-side back pressure chamber Cp is grooved through the expansion-side pilot orifice Pe. 8h. The pressure side chamber member 11 is in close contact with the upper end in FIG. 3 in contact with the flange 8 b of the piston holder 8. The groove 8h is formed by the piston 2, shims 61 and 65, the extension side stopper 67 and the compression side stopper 63, the extension side chamber member 12 and the compression side chamber member 11 mounted on the holding shaft 8a, and the extension side chamber R1 and the pressure side chamber R2. Communication has been cut off. Further, the diameter of the inner periphery of the upper end in FIG. 3 of the spacer 111 is increased, an annular gap is formed between the spacer 111 and the holding shaft 8a, and the groove 8h is provided in the piston holder 8 through the gap. Port 8e. Therefore, the groove 8h communicates with the accommodating portion L through the port 8e, is connected to the adjustment passage Pc, and extends through the compression side pilot orifice Pp and through the expansion side pilot orifice Pe and the compression side back pressure chamber through the extension side pilot orifice Pe. Connected to Cp. As described above, the groove 8h forms a communication path that communicates with the expansion-side back pressure chamber Ce via the compression-side resistance element and also communicates with the compression-side back pressure chamber Cp via the expansion-side resistance element.
　戻って、圧側チャンバ部材１１におけるスペーサ１１１とシム６１との間には、圧側ストッパ６３を介装してあるが、圧側ストッパ６３を廃止してスペーサ１１１をストッパとして機能させて圧側環状プレート６２の移動下限を規制するようにしてもよい。 Returning, the pressure side stopper 63 is interposed between the spacer 111 and the shim 61 in the pressure side chamber member 11, but the pressure side stopper 63 is abolished so that the spacer 111 functions as a stopper. You may make it regulate a movement minimum.
　摺接筒１１２内には、圧側スプールＳｐが収容される。圧側スプールＳｐは、外周を摺接筒１１２における筒部１１２ａの内周に摺接させており、当該摺接筒１１２内で軸方向へ移動できるようになっている。圧側スプールＳｐは、環状のスプール本体１７と、スプール本体１７の図３中下端外周から立ち上がる環状突起１８とを備えている。この環状突起１８の内径は、圧側環状プレート６２の外径よりも小径に設定されており、環状突起１８が圧側環状プレート６２の背面となる図３中上面に当接できるようになっている。 In the sliding contact cylinder 112, a compression side spool Sp is accommodated. The pressure side spool Sp is in sliding contact with the inner periphery of the cylindrical portion 112 a of the sliding contact cylinder 112, and can move in the axial direction within the sliding contact cylinder 112. The pressure-side spool Sp includes an annular spool body 17 and an annular protrusion 18 that rises from the outer periphery of the lower end of the spool body 17 in FIG. The inner diameter of the annular protrusion 18 is set to be smaller than the outer diameter of the pressure-side annular plate 62 so that the annular protrusion 18 can come into contact with the upper surface in FIG.
　なお、スプール本体１７の内径は、スペーサ１１１の外径より大きくしているが、前記内径をスペーサ１１１の外周に摺接する径に設定して、圧側背圧室Ｃｐを圧側スプールＳｐで封じてもよい。 Although the inner diameter of the spool body 17 is larger than the outer diameter of the spacer 111, the inner diameter may be set to a diameter that is in sliding contact with the outer periphery of the spacer 111, and the compression-side back pressure chamber Cp may be sealed with the compression-side spool Sp. Good.
　さらに、圧側チャンバ部材１１の摺接筒１１２には、フランジ１１２ｂを貫通して圧側背圧室Ｃｐと伸側室Ｒ１とを連通する伸側圧力導入通路Ｉｅが設けられている。摺接筒１１２のフランジ１１２ｂの図３中下端には、環状弁体１９が重ねてあり、この環状弁体１９と圧側スプールＳｐにおけるスプール本体１７との間に介装されたばね２０によって環状弁体１９がフランジ１１２ｂへ押しつけられている。また、伸側圧力導入通路Ｉｅは、通過液体の流れに対して抵抗を生じさせないように配慮されている。 Further, the sliding contact cylinder 112 of the compression side chamber member 11 is provided with an expansion side pressure introduction passage Ie that passes through the flange 112b and communicates the compression side back pressure chamber Cp and the expansion side chamber R1. An annular valve body 19 is superimposed on the lower end of the flange 112b of the sliding contact cylinder 112 in FIG. 3, and an annular valve body is provided by a spring 20 interposed between the annular valve body 19 and the spool body 17 of the compression side spool Sp. 19 is pressed against the flange 112b. Further, the extension side pressure introduction passage Ie is considered so as not to cause resistance to the flow of the passing liquid.
　この環状弁体１９は、緩衝器Ｄの伸長作動時において、伸側室Ｒ１が圧縮されて圧力が高まると、この圧力によって押圧されてフランジ１１２ｂから離座して伸側圧力導入通路Ｉｅを開放する。また、圧側背圧室Ｃｐ内の圧力が伸側室Ｒ１より高くなる緩衝器Ｄの収縮作動時にはフランジ１１２ｂに押しつけられて伸側圧力導入通路Ｉｅを閉塞し、伸側室Ｒ１からの液体の流れのみを許容する。このように、環状弁体１９とばね２０は、伸側逆止弁Ｔｅを構成しており、伸側圧力導入通路Ｉｅを伸側室Ｒ１から圧側背圧室Ｃｐへ向かう液体の流れのみを許容する一方通行の通路に設定している。 When the expansion side chamber R1 is compressed and the pressure increases during the expansion operation of the shock absorber D, the annular valve body 19 is pressed by this pressure and is separated from the flange 112b to open the expansion side pressure introduction passage Ie. . Further, during the contraction operation of the shock absorber D in which the pressure in the compression side back pressure chamber Cp becomes higher than that of the expansion side chamber R1, it is pressed against the flange 112b to close the expansion side pressure introduction passage Ie, and only the flow of liquid from the expansion side chamber R1 is performed. Allow. As described above, the annular valve body 19 and the spring 20 constitute the extension-side check valve Te, and only allow the flow of liquid from the extension-side chamber R1 toward the compression-side back pressure chamber Cp through the extension-side pressure introduction passage Ie. It is set as a one-way passage.
　ばね２０は、環状弁体１９をフランジ１１２ｂに押し付ける役割を担って、環状弁体１９とともに伸側逆止弁Ｔｅを構成するとともに、圧側スプールＳｐを圧側リーフバルブＶｐへ向けて附勢する役割をも担っている。よって、圧側リーフバルブＶｐが撓んで圧側スプールＳｐがピストン２から離間する方向へ押し上げられてから圧側リーフバルブＶｐの撓みが解消すると、ばね２０のばね力で圧側スプールＳｐが速やかに元の位置（図３に示す位置）へ戻る。圧側スプールＳｐの附勢を別途のばねで附勢できるが、伸側逆止弁Ｔｅとばね２０を共用でき部品点数を削減できるとともに構造が簡単となる利点がある。なお、圧側スプールＳｐの外径は、環状突起１８の内径よりも大径に設定されていて、環状突起１８が圧側環状プレート６２に当接するようになっているので、圧側スプールＳｐは圧側背圧室Ｃｐの圧力によって常に圧側リーフバルブＶｐへ向けて附勢される。 The spring 20 plays a role of pressing the annular valve body 19 against the flange 112b, constitutes an extension check valve Te together with the annular valve body 19, and plays a role of urging the pressure side spool Sp toward the pressure side leaf valve Vp. Also bears. Therefore, when the pressure-side leaf valve Vp is bent and the pressure-side spool Sp is pushed up in the direction away from the piston 2 and the bending of the pressure-side leaf valve Vp is eliminated, the pressure-side spool Sp is quickly returned to the original position (by the spring force of the spring 20). Return to the position shown in FIG. Although the pressure side spool Sp can be biased by a separate spring, there is an advantage that the extension side check valve Te and the spring 20 can be shared, the number of parts can be reduced, and the structure can be simplified. The outer diameter of the pressure side spool Sp is set to be larger than the inner diameter of the annular protrusion 18 so that the annular protrusion 18 comes into contact with the pressure side annular plate 62. The pressure in the chamber Cp is always urged toward the compression side leaf valve Vp.
　なお、伸側スプールＳｅの伸側背圧室Ｃｅの圧力を受ける受圧面積は、伸側スプールＳｅの外径を直径とする円の面積から環状突起１４の内径を直径とする円の面積の差分となる。同様に圧側スプールＳｐの圧側背圧室Ｃｐの圧力を受ける受圧面積は、圧側スプールＳｐの外径を直径とする円の面積から環状突起１８の内径を直径とする円の面積の差分となる。 In addition, the pressure receiving area which receives the pressure of the extension side back pressure chamber Ce of the extension side spool Se is a difference between the area of a circle whose diameter is the outer diameter of the extension side spool Se and the area of the circle whose diameter is the inner diameter of the annular protrusion 14. It becomes. Similarly, the pressure receiving area that receives the pressure of the pressure side back pressure chamber Cp of the pressure side spool Sp is a difference between the area of the circle having the outer diameter of the pressure side spool Sp as the diameter and the area of the circle having the inner diameter of the annular protrusion 18 as the diameter.
　また、伸側環状プレート６６に伸側背圧室Ｃｅの圧力が直接的に作用する受圧面積は、環状突起１４の内径を直径とする円の面積からシム６５の外径を直径とする円の面積を除いた面積となる。よって、伸側スプールＳｅの外径を直径とする円の面積からシム６５の外径を直径とする円の面積を除いた面積に伸側背圧室Ｃｅの圧力を乗じた力が伸側荷重として伸側リーフバルブＶｅに作用する。そして、伸側リーフバルブＶｅは、伸側荷重によってピストン２へ向けて附勢される。なお、伸側環状プレート６６を廃止して伸側リーフバルブＶｅの背面に環状突起１４を直接当接させてもよい。この場合も、伸側リーフバルブＶｅがシム６５の外周に装着されているので、伸側環状プレート６６を設ける場合と同じ伸側荷重が伸側リーフバルブＶｅに作用する。 Further, the pressure receiving area where the pressure of the expansion side back pressure chamber Ce directly acts on the expansion side annular plate 66 is from the area of a circle whose diameter is the inner diameter of the annular protrusion 14 to the circle whose diameter is the outer diameter of the shim 65. It is the area excluding the area. Therefore, the force obtained by multiplying the area obtained by subtracting the area of the circle having the outer diameter of the shim 65 from the area of the circle having the outer diameter of the extension side spool Se as the diameter of the extension side back pressure chamber Ce is the extension side load. Acting on the extension side leaf valve Ve. The extension side leaf valve Ve is biased toward the piston 2 by the extension side load. Note that the extension-side annular plate 66 may be eliminated and the annular protrusion 14 may be brought into direct contact with the back surface of the extension-side leaf valve Ve. Also in this case, since the extension side leaf valve Ve is mounted on the outer periphery of the shim 65, the same extension side load as that when the extension side annular plate 66 is provided acts on the extension side leaf valve Ve.
　他方、圧側環状プレート６２に圧側背圧室Ｃｐの圧力が直接的に作用する受圧面積は、環状突起１８の内径を直径とする円の面積からシム６１の外径を直径とする円の面積を除いた面積となる。よって、圧側スプールＳｐの外径を直径とする円の面積からシム６１の外径を直径とする円の面積を除いた面積に圧側背圧室Ｃｐの圧力を乗じた力が圧側荷重として圧側リーフバルブＶｐに作用する。そして、圧側リーフバルブＶｐは、圧側荷重によってピストン２へ向けて附勢される。なお、圧側環状プレート６２を廃止して圧側リーフバルブＶｐの背面に環状突起１８を直接当接させてもよい。この場合も、圧側リーフバルブＶｐがシム６１の外周に装着されているので、圧側環状プレート６２を設ける場合と同じ圧側荷重が圧側リーフバルブＶｐに作用する。 On the other hand, the pressure receiving area where the pressure of the pressure side back pressure chamber Cp directly acts on the pressure side annular plate 62 is the area of the circle whose diameter is the outer diameter of the shim 61 from the area of the circle whose diameter is the inner diameter of the annular protrusion 18. Excluded area. Therefore, the force obtained by multiplying the area obtained by subtracting the area of the circle having the outer diameter of the shim 61 from the area of the circle having the outer diameter of the compression side spool Sp by the pressure of the compression side back pressure chamber Cp as the compression side load is the compression side leaf. Acts on the valve Vp. The pressure side leaf valve Vp is urged toward the piston 2 by the pressure side load. Note that the pressure side annular plate 62 may be eliminated and the annular protrusion 18 may be brought into direct contact with the back surface of the pressure side leaf valve Vp. Also in this case, since the pressure side leaf valve Vp is mounted on the outer periphery of the shim 61, the same pressure side load as when the pressure side annular plate 62 is provided acts on the pressure side leaf valve Vp.
　なお、伸側背圧室Ｃｅを伸側スプールＳｅで閉鎖して伸側背圧室Ｃｅの圧力を伸側環状プレート６６に直接に作用させない場合には、伸側荷重は伸側スプールＳｅの伸側背圧室Ｃｅの圧力を受ける受圧面積のみによって決まる。圧側も同様に、圧側背圧室Ｃｐを圧側スプールＳｐで閉鎖して圧側背圧室Ｃｐの圧力を圧側環状プレート６２に直接に作用させない場合には、圧側荷重は圧側スプールＳｐの圧側背圧室Ｃｐの圧力を受ける受圧面積のみによって決まる。 When the extension side back pressure chamber Ce is closed by the extension side spool Se and the pressure of the extension side back pressure chamber Ce is not directly applied to the extension side annular plate 66, the extension side load is increased by the extension side spool Se. It is determined only by the pressure receiving area that receives the pressure of the side back pressure chamber Ce. Similarly, when the pressure side back pressure chamber Cp is closed by the pressure side spool Sp and the pressure of the pressure side back pressure chamber Cp is not directly applied to the pressure side annular plate 62, the pressure side load is the pressure side back pressure chamber of the pressure side spool Sp. It depends only on the pressure receiving area that receives the pressure of Cp.
　本例では、伸側スプールＳｅを用いているので、伸側リーフバルブＶｅに作用させる伸側荷重を伸側スプールＳｅの伸側背圧室Ｃｅ内の圧力を受ける受圧面積で設定できる。また、圧側も同様に、圧側スプールＳｐを用いているので、圧側リーフバルブＶｐに作用させる圧側荷重を圧側スプールＳｐの圧側背圧室Ｃｐ内の圧力を受ける受圧面積で設定できる。本例では、圧側スプールＳｐと伸側スプールＳｅの受圧面積を等しくしてあるが、前記受圧面積の設定により伸側荷重と圧側荷重に差を持たせられる。 In this example, since the expansion side spool Se is used, the expansion side load acting on the expansion side leaf valve Ve can be set by the pressure receiving area that receives the pressure in the expansion side back pressure chamber Ce of the expansion side spool Se. Similarly, since the pressure side spool Sp is used on the pressure side, the pressure side load acting on the pressure side leaf valve Vp can be set by the pressure receiving area that receives the pressure in the pressure side back pressure chamber Cp of the pressure side spool Sp. In this example, the pressure receiving areas of the compression side spool Sp and the expansion side spool Se are made equal, but the difference between the expansion side load and the compression side load can be given by setting the pressure receiving area.
　続いて、伸側背圧室Ｃｅと圧側背圧室Ｃｐを連通する溝８ｈで形成される連通路の下流と、伸側排出通路Ｅｅ及び圧側排出通路Ｅｐの上流を接続する調節通路Ｐｃが設けられている。調節通路Ｐｃの途中には、電磁圧力制御弁６が設けられていて、上流の伸側背圧室Ｃｅ及び圧側背圧室Ｃｐの圧力を制御できるようになっている。 Subsequently, an adjustment passage Pc is provided to connect the downstream side of the communication passage formed by the groove 8h that connects the extension side back pressure chamber Ce and the pressure side back pressure chamber Cp, and the upstream side of the extension side discharge passage Ee and the pressure side discharge passage Ep. It has been. An electromagnetic pressure control valve 6 is provided in the middle of the adjustment passage Pc so that the pressures in the upstream extension-side back pressure chamber Ce and the pressure-side back pressure chamber Cp can be controlled.
　電磁圧力制御弁６は、この実施の形態では、非通電時に調節通路Ｐｃを閉じるとともに通電時に圧力制御を行う。また、調節通路Ｐｃの途中には、電磁圧力制御弁６を迂回するフェール弁ＦＶが設けられている。 In this embodiment, the electromagnetic pressure control valve 6 closes the adjustment passage Pc when not energized and performs pressure control when energized. A fail valve FV that bypasses the electromagnetic pressure control valve 6 is provided in the middle of the adjustment passage Pc.
　電磁圧力制御弁６は、図１及び図２に示すように、弁収容筒３０ａと制御弁弁座３０ｄとを備えた弁座部材３０と、制御弁弁座３０ｄに離着座する電磁弁弁体３１と、電磁弁弁体３１に推力を与えこれを軸方向に駆動するソレノイドＳｏｌとを備えて構成されている。 As shown in FIGS. 1 and 2, the electromagnetic pressure control valve 6 includes a valve seat member 30 including a valve housing cylinder 30a and a control valve valve seat 30d, and an electromagnetic valve valve body that is attached to and detached from the control valve valve seat 30d. 31 and a solenoid Sol that applies thrust to the solenoid valve body 31 and drives it in the axial direction.
　そして、弁座部材３０は、ピストンホルダ８のソケット８ｃ内に嵌合されて、フランジ８ｂの図２中上端に重ねられる環状のバルブハウジング３２の内周に弁収容筒３０ａを挿入することで径方向へ位置決められつつ、収容部Ｌ内に収容されている。 The valve seat member 30 is fitted into the socket 8c of the piston holder 8, and the diameter of the valve seat member 30 is inserted by inserting the valve housing cylinder 30a into the inner periphery of the annular valve housing 32 that is superimposed on the upper end of the flange 8b in FIG. It is accommodated in the accommodating part L, being positioned in the direction.
　バルブハウジング３２は、図２に示すように、環状であって、図２中上端に設けた環状窓３２ａと、環状窓３２ａから開口して図２中下端に通じるポート３２ｂと、図２中上端内周から開口してポート３２ｂに通じる切欠溝３２ｃと、外周に設けられて軸方向に沿って設けた縦溝３２ｄと、前記環状窓３２ａの外周を囲む環状のフェール弁弁座３２ｅとを備えて構成されている。 As shown in FIG. 2, the valve housing 32 has an annular shape, an annular window 32a provided at the upper end in FIG. 2, a port 32b that opens from the annular window 32a and communicates with the lower end in FIG. 2, and an upper end in FIG. A notch groove 32c that opens from the inner periphery and communicates with the port 32b, a vertical groove 32d that is provided on the outer periphery and extends along the axial direction, and an annular fail valve seat 32e that surrounds the outer periphery of the annular window 32a. Configured.
　このバルブハウジング３２をソケット８ｃ内に挿入してフランジ８ｂの図２中上端に重ねると、ポート３２ｂがポート８ｅのフランジ８ｂの上端に面する開口に対向してポート３２ｂ及び切欠溝３２ｃがポート８ｅに連通され、さらに、縦溝３２ｄがフランジ８ｂに設けた切欠８ｇに対向してこれらが連通されるようになっている。 When the valve housing 32 is inserted into the socket 8c and overlapped with the upper end of the flange 8b in FIG. 2, the port 32b faces the opening facing the upper end of the flange 8b of the port 8e, and the port 32b and the cutout groove 32c have the port 8e. Further, the vertical groove 32d is communicated with the notch 8g provided in the flange 8b.
　よって、ポート３２ｂ及び切欠溝３２ｃは、ポート８ｅを通じて連通路を形成する溝８ｈに連通され、さらには、伸側パイロットオリフィスＰｅ及び圧側パイロットオリフィスＰｐを介して伸側背圧室Ｃｅ及び圧側背圧室Ｃｐに連通される。また、縦溝３２ｄは、切欠８ｇ、縦孔８ｄおよび逆止弁２５で形成される伸側排出通路Ｅｅを通じて圧側室Ｒ２に連通されるとともに、透孔９ｃ、凹部８ｉ、貫通孔８ｊ及び逆止弁２２によって形成される圧側排出通路Ｅｐを通じて伸側室Ｒ１に連通される。 Therefore, the port 32b and the notch groove 32c are communicated with the groove 8h forming the communication path through the port 8e, and further, the expansion side back pressure chamber Ce and the pressure side back pressure are connected via the expansion side pilot orifice Pe and the pressure side pilot orifice Pp. It communicates with the chamber Cp. Further, the vertical groove 32d communicates with the pressure side chamber R2 through the expansion side discharge passage Ee formed by the notch 8g, the vertical hole 8d, and the check valve 25, and the through hole 9c, the recess 8i, the through hole 8j, and the check. The pressure side discharge passage Ep formed by the valve 22 communicates with the extension side chamber R1.
　バルブハウジング３２内には、筒状の弁座部材３０における弁収容筒３０ａが収容されている。この弁座部材３０は、有底筒状であって図２中上端外周にフランジ３０ｂを備えた弁収容筒３０ａと、弁収容筒３０ａの側方から開口して内部へ通じる透孔３０ｃと、弁収容筒３０ａの図２中上端に軸方向へ向けて突出する環状の制御弁弁座３０ｄとを備えて構成されている。 In the valve housing 32, the valve accommodating cylinder 30a in the cylindrical valve seat member 30 is accommodated. The valve seat member 30 has a bottomed cylindrical shape and has a valve accommodating cylinder 30a having a flange 30b on the outer periphery of the upper end in FIG. 2, a through hole 30c that opens from the side of the valve accommodating cylinder 30a and communicates with the inside, An annular control valve seat 30d that protrudes in the axial direction is provided at the upper end in FIG. 2 of the valve housing cylinder 30a.
　また、弁座部材３０の弁収容筒３０ａの外周には、環状のリーフバルブであるフェール弁弁体３３が装着されている。弁収容筒３０ａをバルブハウジング３２に挿入して弁座部材３０をバルブハウジング３２に組み付けると、フェール弁弁体３３は、内周が弁座部材３０におけるフランジ３０ｂとバルブハウジング３２の図２中上端内周とで挟持されて固定される。よって、フェール弁弁体３３は、外周側がバルブハウジング３２に設けた環状のフェール弁弁座３２ｅに初期撓みが与えられた状態で着座し、環状窓３２ａを閉塞する。このフェール弁弁体３３は、ポート３２ｂを通じて環状窓３２ａ内に作用する圧力が開弁圧に達すると撓んで、環状窓３２ａを開放してポート３２ｂを伸側排出通路Ｅｅ及び圧側排出通路Ｅｐへ連通させる。そして、フェール弁弁体３３とフェール弁弁座３２ｅとでフェール弁ＦＶを形成している。 Further, on the outer periphery of the valve housing cylinder 30a of the valve seat member 30, a fail valve body 33 which is an annular leaf valve is mounted. When the valve housing cylinder 30a is inserted into the valve housing 32 and the valve seat member 30 is assembled to the valve housing 32, the fail valve body 33 has an inner periphery that is the flange 30b of the valve seat member 30 and the upper end of the valve housing 32 in FIG. It is clamped by the inner periphery and fixed. Therefore, the fail valve body 33 is seated in the state where the initial deflection is given to the annular fail valve seat 32e provided on the valve housing 32 on the outer peripheral side, and closes the annular window 32a. The fail valve body 33 bends when the pressure acting in the annular window 32a through the port 32b reaches the valve opening pressure, opens the annular window 32a, and connects the port 32b to the extension side discharge passage Ee and the pressure side discharge passage Ep. Communicate. A fail valve FV is formed by the fail valve body 33 and the fail valve seat 32e.
　また、弁収容筒３０ａをバルブハウジング３２に挿入して弁座部材３０をバルブハウジング３２に組み付けると、バルブハウジング３２に設けた切欠溝３２ｃが弁収容筒３０ａに設けた透孔３０ｃに対向して、伸側背圧室Ｃｅ及び圧側背圧室Ｃｐがポート３２ｂを通じて弁収容筒３０ａ内に連通される。 When the valve housing cylinder 30a is inserted into the valve housing 32 and the valve seat member 30 is assembled to the valve housing 32, the notch groove 32c provided in the valve housing 32 faces the through hole 30c provided in the valve housing cylinder 30a. The extension-side back pressure chamber Ce and the compression-side back pressure chamber Cp are communicated with each other in the valve housing cylinder 30a through the port 32b.
　弁座部材３０の図１中上方には、環状であってフランジ３０ｂの図１中上端に当接する弁固定部材３５が重ねられており、さらに、弁固定部材３５の図１中上方には電磁弁収容筒９内に収容されるソレノイドＳｏｌが配置されている。電磁弁収容筒９にピストンホルダ８を螺着して一体化すると、バルブハウジング３２、フェール弁弁体３３、弁座部材３０、弁固定部材３５及びソレノイドＳｏｌが電磁弁収容筒９とピストンホルダ８に挟持されて固定される。なお、弁固定部材３５には、弁座部材３０のフランジ３０ｂに当接しても、弁固定部材３５の内周側の空間が弁座部材３０の外周側の空間に連通できるように切欠溝３５ａが設けられている。この連通は、切欠溝３５ａではなく、ポートなどの孔で行うようにしてもよい。 A valve fixing member 35 that is annular and contacts the upper end of the flange 30b in FIG. 1 is stacked above the valve seat member 30 in FIG. A solenoid Sol accommodated in the valve accommodating cylinder 9 is disposed. When the piston holder 8 is screwed and integrated with the electromagnetic valve housing cylinder 9, the valve housing 32, the fail valve valve body 33, the valve seat member 30, the valve fixing member 35 and the solenoid Sol are connected to the electromagnetic valve housing cylinder 9 and the piston holder 8. It is pinched and fixed. Note that the valve fixing member 35 has a notch groove 35 a so that the inner circumferential space of the valve fixing member 35 can communicate with the outer circumferential space of the valve seat member 30 even when abutting against the flange 30 b of the valve seat member 30. Is provided. This communication may be performed not by the notch groove 35a but by a hole such as a port.
　ソレノイドＳｏｌは、巻線３７と巻線３７に通電するハーネスＨとをモールド樹脂で一体化した有頂筒状のモールドステータ３６と、有頂筒状であってモールドステータ３６の内周に嵌合される第一固定鉄心３８と、モールドステータ３６の図１中下端に重ねられる環状の第二固定鉄心３９と、第一固定鉄心３８と第二固定鉄心３９との間に介装されて磁気的な空隙を形成するフィラーリング４０と、第一固定鉄心３８と第二固定鉄心３９の内周側に軸方向移動可能に配置された筒状の可動鉄心４１と、可動鉄心４１の内周に固定されるシャフト４２とを備えて構成されている。ソレノイドＳｏｌは、巻線３７への通電により、可動鉄心４１を吸引してシャフト４２に図２中下方向きの推力を与える。シャフト４２は、電磁弁弁体３１に当接しており、ソレノイドＳｏｌは、通電時に電磁弁弁体３１に図２中下向きの推力を与えるようになっている。 The solenoid Sol is a top-cylindrical molded stator 36 in which a winding 37 and a harness H that energizes the winding 37 are integrated with a mold resin, and a top-cylindrical cylindrical stator that is fitted to the inner periphery of the mold stator 36. The first fixed iron core 38, the annular second fixed iron core 39 superimposed on the lower end in FIG. 1 of the molded stator 36, and the first fixed iron core 38 and the second fixed iron core 39 are magnetically interposed. Fixed to the inner periphery of the movable core 41, the filler ring 40 that forms a gap, the cylindrical movable core 41 that is axially movable on the inner peripheral side of the first fixed core 38 and the second fixed core 39. And a shaft 42 to be configured. The solenoid Sol attracts the movable iron core 41 by energizing the winding 37 and applies a downward thrust to the shaft 42 in FIG. The shaft 42 is in contact with the electromagnetic valve body 31, and the solenoid Sol applies a downward thrust in FIG. 2 to the electromagnetic valve body 31 when energized.
　さらに、弁座部材３０内には、電磁弁弁体３１が摺動自在に挿入されている。電磁弁弁体３１は、詳しくは、弁座部材３０における弁収容筒３０ａ内に摺動自在に挿入される小径部３１ａと、小径部３１ａの図２中上方側である反弁座部材側に設けられて弁収容筒３０ａには挿入されない大径部３１ｂと、小径部３１ａと大径部３１ｂとの間に設けた環状の凹部３１ｃと、大径部３１ｂの反弁座部材側端の外周に設けたフランジ状のばね受部３１ｄと、電磁弁弁体３１の先端から後端へ貫通する連絡路３１ｅ、連絡路３１ｅの途中に設けたオリフィス３１ｆとを備えて構成されている。 Furthermore, a solenoid valve body 31 is slidably inserted into the valve seat member 30. Specifically, the solenoid valve body 31 is provided on the side of the valve seat member 30 that is slidably inserted into the valve housing cylinder 30a of the valve seat member 30 and the counter valve seat member side that is the upper side of the small diameter portion 31a in FIG. A large-diameter portion 31b that is provided and is not inserted into the valve housing cylinder 30a, an annular recess 31c provided between the small-diameter portion 31a and the large-diameter portion 31b, and an outer periphery of the counter-valve seat member side end of the large- diameter portion 31b 31d, a connecting passage 31e penetrating from the front end to the rear end of the solenoid valve body 31, and an orifice 31f provided in the middle of the connecting passage 31e.
　また、電磁弁弁体３１には、前述のように、凹部３１ｃを境にして反弁座部材側の外径を小径部３１ａより大径として大径部３１ｂが形成されている。電磁弁弁体３１は、大径部３１ｂの図２中下端に制御弁弁座３０ｄに対向する着座部３１ｇを備えており、弁座部材３０に対して軸方向へ移動すると着座部３１ｇが制御弁弁座３０ｄに離着座する。つまり、電磁弁弁体３１と弁座部材３０とを備えて電磁圧力制御弁６が構成されており、着座部３１ｇが制御弁弁座３０ｄに着座すると電磁圧力制御弁６が閉弁する。 Further, as described above, the solenoid valve body 31 is formed with the large-diameter portion 31b with the outer diameter on the side opposite to the valve seat member larger than the small-diameter portion 31a with the recess 31c as a boundary. The electromagnetic valve body 31 includes a seating portion 31g facing the control valve valve seat 30d at the lower end in FIG. 2 of the large-diameter portion 31b, and the seating portion 31g is controlled when moved in the axial direction with respect to the valve seat member 30. The valve seat 30d is detached and seated. That is, the electromagnetic pressure control valve 6 includes the electromagnetic valve body 31 and the valve seat member 30. When the seating portion 31g is seated on the control valve valve seat 30d, the electromagnetic pressure control valve 6 is closed.
　さらに、弁座部材３０のフランジ３０ｂとばね受部３１ｄとの間には、電磁弁弁体３１を弁座部材３０から離間する方向へ附勢するコイルばね３４が介装されている。したがって、電磁弁弁体３１は、コイルばね３４によって常に弁座部材３０から離間する方向へ附勢されており、ソレノイドＳｏｌからのコイルばね３４に対抗する推力が作用しないと、弁座部材３０から最も離間する位置に位置決められる。なお、この場合、コイルばね３４を利用して、電磁弁弁体３１を弁座部材３０から離間させる方向へ附勢するようにしているが、コイルばね３４以外にも附勢力を発揮することができる弾性体を使用できる。 Further, a coil spring 34 is interposed between the flange 30b of the valve seat member 30 and the spring receiving portion 31d to urge the electromagnetic valve valve body 31 in a direction away from the valve seat member 30. Therefore, the electromagnetic valve body 31 is always urged in the direction away from the valve seat member 30 by the coil spring 34, and if a thrust force against the coil spring 34 from the solenoid Sol does not act, It is positioned at the most distant position. In this case, the coil spring 34 is used to urge the solenoid valve valve body 31 in the direction away from the valve seat member 30, but the urging force can be exerted in addition to the coil spring 34. An elastic body that can be used can be used.
　そして、電磁弁弁体３１は、弁座部材３０に対して最も離間すると、透孔３０ｃに小径部３１ａを対向させて透孔３０ｃを閉塞する。ソレノイドＳｏｌに通電して電磁弁弁体３１を弁座部材３０から最も離間する位置から弁座部材３０側へ所定量移動させると、常に、電磁弁弁体３１は、凹部３１ｃを透孔３０ｃに対向させて透孔３０ｃを開放するようになっている。 When the solenoid valve body 31 is farthest from the valve seat member 30, the small diameter portion 31a is opposed to the through hole 30c to close the through hole 30c. When the solenoid Sol is energized to move the solenoid valve valve 31 by a predetermined amount from the position farthest away from the valve seat member 30 to the valve seat member 30 side, the solenoid valve valve 31 always places the recess 31c into the through hole 30c. The through holes 30c are opened so as to face each other.
　電磁弁弁体３１が透孔３０ｃを開放し、着座部３１ｇが制御弁弁座３０ｄから離座すると透孔３０ｃが電磁弁弁体３１の凹部３１ｃ及び弁固定部材３５に設けた切欠溝３５ａを通じて伸側排出通路Ｅｅ及び圧側排出通路Ｅｐに連通される。そして、ソレノイドＳｏｌの推力を調節すると、電磁弁弁体３１を弁座部材３０側へ附勢する力を制御でき、電磁圧力制御弁６の上流の圧力の作用とコイルばね３４による電磁弁弁体３１を押上げる力がソレノイドＳｏｌによる電磁弁弁体３１を押下げる力を上回ると電磁圧力制御弁６は開弁する。このように、電磁圧力制御弁６の上流側の圧力をソレノイドＳｏｌの推力に応じて制御できる。そして、電磁圧力制御弁６の上流は、調節通路Ｐｃを介して伸側背圧室Ｃｅ及び圧側背圧室Ｃｐに通じているので、この電磁圧力制御弁６によって伸側背圧室Ｃｅ及び圧側背圧室Ｃｐの圧力を制御できる。よって、ソレノイドＳｏｌへの通電量によって、伸側背圧室Ｃｅ及び圧側背圧室Ｃｐの圧力を調節して、伸側荷重および圧側荷重を制御できる。また、電磁圧力制御弁６の下流は、伸側排出通路Ｅｅ及び圧側排出通路Ｅｐに通じており、電磁圧力制御弁６を通過した液体は、緩衝器Ｄの伸長作動時には低圧側の圧側室Ｒ２へ、緩衝器Ｄの収縮作動時には低圧側の伸側室Ｒ１へ排出される。よって、調節通路Ｐｃは、前記したポート８ｅ、ポート３２ｂ、切欠溝３２ｃ、収容部Ｌの一部、縦溝３２ｄによって形成される。 When the solenoid valve body 31 opens the through hole 30c and the seating portion 31g is separated from the control valve valve seat 30d, the through hole 30c passes through the recess 31c of the solenoid valve valve body 31 and the notch groove 35a provided in the valve fixing member 35. The expansion side discharge passage Ee and the pressure side discharge passage Ep are communicated. When the thrust of the solenoid Sol is adjusted, it is possible to control the force that biases the solenoid valve valve body 31 toward the valve seat member 30, and the action of the pressure upstream of the solenoid pressure control valve 6 and the solenoid valve valve body by the coil spring 34. When the force for pushing up 31 exceeds the force for pushing down the solenoid valve valve 31 by the solenoid Sol, the solenoid pressure control valve 6 opens. Thus, the pressure on the upstream side of the electromagnetic pressure control valve 6 can be controlled according to the thrust of the solenoid Sol. Since the upstream side of the electromagnetic pressure control valve 6 communicates with the expansion side back pressure chamber Ce and the pressure side back pressure chamber Cp via the adjustment passage Pc, the electromagnetic pressure control valve 6 causes the expansion side back pressure chamber Ce and the pressure side to communicate with each other. The pressure in the back pressure chamber Cp can be controlled. Therefore, the expansion side load and the compression side load can be controlled by adjusting the pressures of the expansion side back pressure chamber Ce and the compression side back pressure chamber Cp according to the energization amount to the solenoid Sol. Further, the downstream side of the electromagnetic pressure control valve 6 communicates with the expansion side discharge passage Ee and the pressure side discharge passage Ep, and the liquid that has passed through the electromagnetic pressure control valve 6 causes the pressure side chamber R2 on the low pressure side during the expansion operation of the shock absorber D. When the shock absorber D is contracted, it is discharged into the low-pressure side expansion chamber R1. Therefore, the adjustment passage Pc is formed by the port 8e, the port 32b, the notch groove 32c, a part of the accommodating portion L, and the vertical groove 32d.
　また、電磁圧力制御弁６は、ソレノイドＳｏｌへ通電できないフェール時には、弁座部材３０における透孔３０ｃを電磁弁弁体３１における小径部３１ａで閉塞する遮断ポジションを備えている。よって、電磁圧力制御弁６は、圧力制御弁としてだけではなく、開閉弁としても機能する。フェール弁ＦＶは、ポート３２ｂに通じる環状窓３２ａを開閉するようになっていて、その開弁圧が電磁圧力制御弁６の制御可能な上限圧を超える圧力に設定されており、電磁圧力制御弁６を迂回してポート３２ｂを伸側排出通路Ｅｅ及び圧側排出通路Ｅｐに連通する。よって、電磁圧力制御弁６の上流側の圧力が制御上限圧を超えるような場合、フェール弁ＦＶが開弁して伸側背圧室Ｃｅ及び圧側背圧室Ｃｐの圧力をフェール弁ＦＶの開弁圧に制御できる。したがって、たとえば、フェール時において電磁圧力制御弁６が遮断ポジションをとっている場合には、伸側背圧室Ｃｅ及び圧側背圧室Ｃｐの圧力はフェール弁ＦＶの開弁圧に制御される。 Further, the electromagnetic pressure control valve 6 has a blocking position in which the through hole 30c in the valve seat member 30 is closed by the small diameter portion 31a in the electromagnetic valve body 31 during a failure in which the solenoid Sol cannot be energized. Therefore, the electromagnetic pressure control valve 6 functions not only as a pressure control valve but also as an on-off valve. The fail valve FV opens and closes an annular window 32a that communicates with the port 32b, and the valve opening pressure is set to a pressure that exceeds the upper limit pressure that can be controlled by the electromagnetic pressure control valve 6. The electromagnetic pressure control valve 6, the port 32b is communicated with the expansion side discharge passage Ee and the pressure side discharge passage Ep. Therefore, when the pressure on the upstream side of the electromagnetic pressure control valve 6 exceeds the control upper limit pressure, the fail valve FV is opened, and the pressures in the extension-side back pressure chamber Ce and the pressure-side back pressure chamber Cp are opened. The valve pressure can be controlled. Therefore, for example, when the electromagnetic pressure control valve 6 is in the shut-off position at the time of failure, the pressures in the extension side back pressure chamber Ce and the pressure side back pressure chamber Cp are controlled to the valve opening pressure of the fail valve FV.
　さらに、電磁弁弁体３１は、弁座部材３０の弁収容筒３０ａ内に挿入されると、弁収容筒３０ａ内であって透孔３０ｃより先端側に空間Ｋを形成する。この空間Ｋは、電磁弁弁体３１に設けた連絡路３１ｅ及びオリフィス３１ｆを介して電磁弁弁体外に連通されている。これにより、電磁弁弁体３１が弁座部材３０に対して図２中上下方向である軸方向に移動する際、前記空間Ｋがダッシュポットとして機能して、電磁弁弁体３１の急峻な変位を抑制するとともに、電磁弁弁体３１の振動的な動きを抑制できる。 Furthermore, when the solenoid valve body 31 is inserted into the valve housing cylinder 30a of the valve seat member 30, a space K is formed in the valve housing cylinder 30a and on the tip side from the through hole 30c. The space K communicates with the outside of the solenoid valve valve body through a communication path 31e provided in the solenoid valve valve body 31 and an orifice 31f. Thereby, when the solenoid valve valve body 31 moves in the axial direction which is the vertical direction in FIG. 2 with respect to the valve seat member 30, the space K functions as a dashpot, and the solenoid valve valve body 31 is rapidly displaced. And the vibrational movement of the solenoid valve body 31 can be suppressed.
　つづいて、緩衝器Ｄの作動について説明する。まず、緩衝器Ｄが伸長する場合について説明する。緩衝器Ｄが伸長してピストン２が図１中上方へ移動すると、圧縮される伸側室Ｒ１から拡大される圧側室Ｒ２へ液体が伸側リーフバルブＶｅを押して伸側通路３を通過して移動しようとする。 Next, the operation of the shock absorber D will be described. First, the case where the shock absorber D extends will be described. When the shock absorber D extends and the piston 2 moves upward in FIG. 1, the liquid moves from the compressed expansion side chamber R <b> 1 to the expanded pressure side chamber R <b> 2 through the expansion side passage 3 by pushing the expansion side leaf valve Ve. try to.
　また、伸側室Ｒ１内の液体は、伸側逆止弁Ｔｅを押し開いて伸側圧力導入通路Ｉｅを通過し、調節通路Ｐｃへ流れる。調節通路Ｐｃを通過した液体は、逆止弁２５を押し開いて伸側排出通路Ｅｅを介して低圧側の圧側室Ｒ２へ排出される。なお、伸側パイロットオリフィスＰｅは、液体の通過の際に抵抗を与えて圧力損失をもたらし、液体が流れている状態において調節通路Ｐｃの下流では伸側室Ｒ１よりも低圧となるため、圧側排出通路Ｅｐに設けた逆止弁２２は開かず閉塞されたままとなる。 Also, the liquid in the extension side chamber R1 pushes open the extension side check valve Te, passes through the extension side pressure introduction passage Ie, and flows into the adjustment passage Pc. The liquid that has passed through the adjustment passage Pc pushes the check valve 25 open and is discharged to the low pressure side pressure side chamber R2 through the extension side discharge passage Ee. The expansion side pilot orifice Pe gives a resistance when the liquid passes and causes a pressure loss. Since the liquid is flowing, the expansion side pilot orifice Pe has a lower pressure than the expansion side chamber R1 downstream of the adjustment passage Pc. The check valve 22 provided on Ep remains closed without opening.
　伸側圧力導入通路Ｉｅは、圧側背圧室Ｃｐに通じるだけでなく、溝８ｈを介して伸側背圧室Ｃｅにも通じるが、圧側圧力導入通路Ｉｐが圧側逆止弁Ｔｐによって閉塞されるため、緩衝器Ｄの伸長作動時において伸側背圧室Ｃｅ内の圧力は圧側室Ｒ２より高くなる。なお、圧側背圧室Ｃｐの圧力は、低圧側の圧側室Ｒ２よりも高くなるが、液体の流れが生じない圧側通路４を閉塞する圧側リーフバルブＶｐを附勢するだけであるから不都合はない。 The expansion-side pressure introduction passage Ie not only communicates with the compression-side back pressure chamber Cp but also communicates with the expansion-side back pressure chamber Ce through the groove 8h, but the compression-side pressure introduction passage Ip is closed by the compression-side check valve Tp. Therefore, when the shock absorber D is extended, the pressure in the extension side back pressure chamber Ce is higher than that of the compression side chamber R2. The pressure in the pressure side back pressure chamber Cp is higher than that in the pressure side chamber R2 on the low pressure side, but there is no inconvenience because it only energizes the pressure side leaf valve Vp that closes the pressure side passage 4 where no liquid flows. .
　調節通路Ｐｃには、前記したように電磁圧力制御弁６が設けてあり、電磁圧力制御弁６のソレノイドＳｏｌに通電して、調節通路Ｐｃの上流側の圧力を制御してやれば、伸側背圧室Ｃｅ内の圧力を調整して伸側荷重を所望の荷重に制御できる。伸側リーフバルブＶｅには、電磁圧力制御弁６によって制御される伸側荷重が閉弁方向に、伸側通路３を通じて伸側室Ｒ１の圧力が開弁方向に作用する。 As described above, the electromagnetic pressure control valve 6 is provided in the adjustment passage Pc, and if the solenoid Sol of the electromagnetic pressure control valve 6 is energized to control the pressure on the upstream side of the adjustment passage Pc, the extension side back pressure is increased. The extension side load can be controlled to a desired load by adjusting the pressure in the chamber Ce. On the extension side leaf valve Ve, the extension side load controlled by the electromagnetic pressure control valve 6 acts in the valve closing direction, and the pressure in the extension side chamber R1 acts in the valve opening direction through the extension side passage 3.
　伸側リーフバルブＶｅは、伸側荷重を伸側室Ｒ１の圧力の作用による力が上回ると開弁して、両者がバランスする位置までシム６５の外周をスライドしてピストン２から後退する。このように、伸側リーフバルブＶｅがピストン２から離間する後退量は、伸側荷重に応じて決まるので、ソレノイドＳｏｌへの通電量に応じて前記後退量を制御できる。以上により、電磁圧力制御弁６によって伸側リーフバルブＶｅの開度を制御でき、これによって、緩衝器Ｄの伸長作動を行う際の伸側減衰力を大小調節できる。 The extension-side leaf valve Ve opens when the extension-side load exceeds the force due to the action of the pressure in the extension-side chamber R1, and slides on the outer periphery of the shim 65 to a position where the two balance each other and retracts from the piston 2. As described above, the retraction amount by which the extension-side leaf valve Ve is separated from the piston 2 is determined according to the extension-side load. Therefore, the retraction amount can be controlled according to the energization amount to the solenoid Sol. As described above, the opening degree of the extension side leaf valve Ve can be controlled by the electromagnetic pressure control valve 6, and thereby the extension side damping force when the buffer D is extended can be adjusted in magnitude.
　逆に、緩衝器Ｄが収縮する場合について説明する。緩衝器Ｄが収縮してピストン２が図１中下方へ移動すると、圧縮される圧側室Ｒ２から拡大される伸側室Ｒ１へ液体が圧側リーフバルブＶｐを押して圧側通路４を通過して移動しようとする。 Conversely, the case where the shock absorber D contracts will be described. When the shock absorber D contracts and the piston 2 moves downward in FIG. 1, the liquid tries to move from the compressed pressure side chamber R2 to the expanded side chamber R1 through the pressure side passage 4 by pushing the pressure side leaf valve Vp. To do.
　また、圧側室Ｒ２内の液体は、圧側逆止弁Ｔｐを押し開いて圧側圧力導入通路Ｉｐを通過し、調節通路Ｐｃへ流れる。調節通路Ｐｃを通過した液体は、逆止弁２２を押し開いて圧側排出通路Ｅｐを介して低圧側の伸側室Ｒ１へ排出される。なお、圧側パイロットオリフィスＰｐは、液体の通過の際に抵抗を与えて圧力損失をもたらし、液体が流れている状態において調節通路Ｐｃの下流では圧側室Ｒ２よりも低圧となるため、伸側排出通路Ｅｅに設けた逆止弁２５は開かず閉塞されたままとなる。 Also, the liquid in the pressure side chamber R2 pushes and opens the pressure side check valve Tp, passes through the pressure side pressure introduction passage Ip, and flows to the adjustment passage Pc. The liquid that has passed through the adjustment passage Pc pushes the check valve 22 open and is discharged to the low-pressure-side extension side chamber R1 through the pressure-side discharge passage Ep. Note that the pressure side pilot orifice Pp provides resistance when the liquid passes and causes a pressure loss. In the state where the liquid flows, the pressure side pilot orifice Pp has a pressure lower than the pressure side chamber R2 downstream of the adjustment passage Pc. The check valve 25 provided at Ee is not opened and remains closed.
　圧側圧力導入通路Ｉｐは、伸側背圧室Ｃｅに通じるだけでなく、溝８ｈを介して圧側背圧室Ｃｐにも通じるが、伸側圧力導入通路Ｉｅが伸側逆止弁Ｔｅによって閉塞されるため、緩衝器Ｄの収縮作動時において圧側背圧室Ｃｐ内の圧力は伸側室Ｒ１より高くなる。なお、伸側背圧室Ｃｅの圧力は、低圧側の伸側室Ｒ１よりも高くなるが、液体の流れが生じない伸側通路３を閉塞する伸側リーフバルブＶｅを附勢するだけであるから不都合はない。 The compression-side pressure introduction passage Ip not only communicates with the expansion-side back pressure chamber Ce but also communicates with the compression-side back pressure chamber Cp through the groove 8h, but the expansion-side pressure introduction passage Ie is blocked by the expansion-side check valve Te. Therefore, the pressure in the compression side back pressure chamber Cp becomes higher than that of the expansion side chamber R1 when the shock absorber D is contracted. The pressure in the extension side back pressure chamber Ce is higher than that in the extension side chamber R1 on the low pressure side, but it only energizes the extension side leaf valve Ve that closes the extension side passage 3 where no liquid flows. There is no inconvenience.
　そして、圧側リーフバルブＶｐには、電磁圧力制御弁６によって制御される圧側荷重が閉弁方向に、圧側通路４を通じて圧側室Ｒ２の圧力が開弁方向に作用する。 The pressure side load valve controlled by the electromagnetic pressure control valve 6 acts on the pressure side leaf valve Vp in the valve closing direction, and the pressure in the pressure side chamber R2 acts on the pressure side passage 4 in the valve opening direction.
　よって、圧側リーフバルブＶｐは、圧側荷重を圧側室Ｒ２の圧力の作用による力が上回ると開弁して、両者がバランスする位置までシム６１の外周をスライドしてピストン２から後退する。このように、圧側リーフバルブＶｐがピストン２から離間する後退量は、圧側荷重に応じて決まるので、ソレノイドＳｏｌへの通電量に応じて前記後退量を制御できる。以上により、電磁圧力制御弁６によって圧側リーフバルブＶｐの開度を制御でき、これによって、緩衝器Ｄの収縮作動を行う際の圧側減衰力を大小調節できる。 Therefore, the pressure-side leaf valve Vp opens when the force due to the action of the pressure in the pressure-side chamber R2 exceeds the pressure-side load, slides on the outer periphery of the shim 61 to a position where both balance, and moves backward from the piston 2. As described above, the retraction amount by which the pressure-side leaf valve Vp is separated from the piston 2 is determined according to the pressure-side load. Therefore, the retraction amount can be controlled according to the energization amount to the solenoid Sol. As described above, the opening degree of the pressure side leaf valve Vp can be controlled by the electromagnetic pressure control valve 6, whereby the pressure side damping force when the shock absorber D is contracted can be adjusted in magnitude.
　前述したように、本例の緩衝器Ｄでは、伸側リーフバルブＶｅの外径が圧側リーフバルブＶｐの外径よりも小径とされており、伸側リーフバルブＶｅの伸側室Ｒ１の圧力を受ける受圧面積は、圧側リーフバルブＶｐの圧側室Ｒ２の圧力を受ける受圧面積よりも小さい。そのため、電磁圧力制御弁６で伸側荷重と圧側荷重を同じにしても、伸側リーフバルブＶｅの開弁圧は圧側リーフバルブＶｐの開弁圧よりも大きくなり、伸側減衰力を圧側減衰力より大きくできる。 As described above, in the shock absorber D of this example, the outer diameter of the extension side leaf valve Ve is smaller than the outer diameter of the compression side leaf valve Vp, and receives the pressure of the extension side chamber R1 of the extension side leaf valve Ve. The pressure receiving area is smaller than the pressure receiving area that receives the pressure of the pressure side chamber R2 of the pressure side leaf valve Vp. Therefore, even if the extension side load and the compression side load are the same in the electromagnetic pressure control valve 6, the valve opening pressure of the extension side leaf valve Ve becomes larger than the valve opening pressure of the compression side leaf valve Vp, and the extension side damping force is reduced to the compression side. Can be greater than force.
　そして、本発明の緩衝器Ｄでは、伸側背圧室Ｃｅおよび圧側背圧室Ｃｐを連通する連通路がピストンホルダ８の保持軸８ａの外周に設けられているので、保持軸８ａ内に連通路を設けるためのセパレータを設ける必要がない。よって、本発明の緩衝器Ｄによれば、連通路の形成にセパレータが不要となり、部品点数が削減されコストを低減でき、保持軸８ａ内にセパレータを設けずに済むため縦孔８ｄの径を小径にできるので、ピストンホルダ８の強度を確保できる。 In the shock absorber D of the present invention, the communication path that communicates the extension-side back pressure chamber Ce and the pressure-side back pressure chamber Cp is provided on the outer periphery of the holding shaft 8a of the piston holder 8, and therefore communicates with the holding shaft 8a. There is no need to provide a separator for providing the passage. Therefore, according to the shock absorber D of the present invention, a separator is not required for forming the communication path, the number of parts can be reduced, the cost can be reduced, and the separator 8 is not provided in the holding shaft 8a, so the diameter of the vertical hole 8d can be reduced. Since the diameter can be reduced, the strength of the piston holder 8 can be secured.
　さらに、セパレータを設ける場合、保持軸８ａとセパレータとの間に隙間が生じると連通路から伸側排出通路Ｅｅへ液体が漏れてしまい、製品毎に減衰力特性にばらつきが生じる可能性があった。本緩衝器Ｄでは、保持軸８ａに組付けられるピストン２をはじめとした前記各部品によって、溝８ｈが伸側圧力導入通路Ｉｅおよび圧側圧力導入通路Ｉｐを介さずに伸側室Ｒ１および圧側室Ｒ２に連通しないよう閉鎖される。前記保持軸８ａに組付けられる前記各部品は、ピストンナットとして機能するスペーサ１２１によって軸方向の荷重を受けて密着状態で保持軸８ａに固定されているので、溝８ｈを密に閉鎖できる。よって、本発明の緩衝器Ｄでは、連通路として機能する溝８ｈから伸側室Ｒ１或いは圧側室Ｒ２へ液体が漏れないので、製品ごとに減衰力特性にばらつきが生じるような問題も解消される。 Further, when a separator is provided, if a gap is generated between the holding shaft 8a and the separator, the liquid leaks from the communication path to the extension-side discharge path Ee, and there is a possibility that the damping force characteristic varies among products. . In the present shock absorber D, the groove 8h is not connected to the expansion side pressure introduction passage Ie and the pressure side pressure introduction passage Ip by the above-described components including the piston 2 assembled to the holding shaft 8a. Closed to prevent communication. Each of the components assembled to the holding shaft 8a is fixed to the holding shaft 8a in close contact with the load in the axial direction by the spacer 121 functioning as a piston nut, so that the groove 8h can be closed tightly. Therefore, in the shock absorber D of the present invention, since the liquid does not leak from the groove 8h functioning as the communication path to the extension side chamber R1 or the pressure side chamber R2, the problem that the damping force characteristic varies for each product is solved.
　なお、連通路を形成する溝８ｈの断面形状は任意に設計できる。また、連通路は、本例では、保持軸８ａの外周に設けた溝８ｈで形成されているが、保持軸８ａと保持軸８ａに組付けられる部品との間に連通路を形成する空隙を設ければよいので、たとえば、保持軸８ａの外周に軸方向に沿う面取を形成して、この面取部分で保持軸８ａに組付けられる各部品との間に隙間を設けて連通路を形成してもよい。このようにしても、溝８ｈで連通路を形成する場合と同様の効果が得られる。 In addition, the cross-sectional shape of the groove 8h forming the communication path can be designed arbitrarily. Further, in this example, the communication path is formed by a groove 8h provided on the outer periphery of the holding shaft 8a. However, a gap that forms the communication path is formed between the holding shaft 8a and the parts assembled to the holding shaft 8a. Therefore, for example, a chamfer along the axial direction is formed on the outer periphery of the holding shaft 8a, and a gap is provided between each part assembled to the holding shaft 8a at this chamfered portion to provide a communication path. It may be formed. Even if it does in this way, the effect similar to the case where a communicating path is formed in the groove | channel 8h is acquired.
　また、本例の緩衝器Ｄでは、伸側パイロットオリフィス（伸側抵抗要素）Ｐｅが圧側チャンバ部材１１に設けられ、圧側パイロットオリフィス（圧側抵抗要素）Ｐｐが伸側チャンバ部材１２に設けられている。従来では、ピストンホルダ側に伸側抵抗要素と圧側抵抗要素を設けていたので、たとえば、伸側抵抗要素と圧側抵抗要素がそれぞれ４種類ある場合、これらの全ての組合を実現するには、合計１６種類の異なるピストンホルダを用意しなくてはならなかった。これに対して、伸側抵抗要素と圧側抵抗要素をそれぞれ対応する伸側チャンバ部材１２と圧側チャンバ部材１１に別々に設けると、伸側チャンバ部材１２と圧側チャンバ部材１１をそれぞれ４種類ずつ用意しておけば済む。よって、このように緩衝器Ｄを構成すると、伸側抵抗要素や圧側抵抗要素のチューニングが容易となり、管理すべき部品も少なくて済み、より一層コストを低減できる。 Further, in the shock absorber D of this example, the expansion side pilot orifice (extension side resistance element) Pe is provided in the compression side chamber member 11, and the compression side pilot orifice (pressure side resistance element) Pp is provided in the expansion side chamber member 12. . Conventionally, since the expansion resistance element and the compression resistance element are provided on the piston holder side, for example, when there are four types of expansion resistance elements and compression resistance elements, respectively, in order to realize all these combinations, the total 16 different piston holders had to be prepared. On the other hand, when the extension side resistance element and the compression side resistance element are separately provided in the corresponding extension side chamber member 12 and compression side chamber member 11, four types of extension side chamber member 12 and compression side chamber member 11 are prepared. All you need to do is Therefore, when the shock absorber D is configured in this manner, tuning of the extension side resistance element and the compression side resistance element is facilitated, the number of parts to be managed is reduced, and the cost can be further reduced.
　さらに、本例の緩衝器Ｄでは、ピストンホルダ８の保持軸８ａに圧側室Ｒ２に連通される縦孔８ｄを設けて伸側排出通路Ｅｅが形成されており、縦孔８ｄ内に調節通路Ｐｃから圧側室Ｒ２へ液体の流れのみを許容する逆止弁２５の弁座として機能するパイプ２５ａを設けている。このように緩衝器Ｄを構成すると逆止弁２５の設置に当たって、ピストンホルダ８の保持軸８ａに直接逆止弁２５の弁座を形成する難しい加工を施す必要が無くなる。 Further, in the shock absorber D of the present example, the holding shaft 8a of the piston holder 8 is provided with a vertical hole 8d communicating with the compression side chamber R2, and an expansion side discharge passage Ee is formed, and the adjustment passage Pc is formed in the vertical hole 8d. A pipe 25a that functions as a valve seat for the check valve 25 that allows only the flow of liquid from the pressure side chamber R2 is provided. When the shock absorber D is configured in this manner, it is not necessary to perform difficult processing for directly forming the valve seat of the check valve 25 on the holding shaft 8a of the piston holder 8 when the check valve 25 is installed.
　なお、本例の緩衝器Ｄにあっては、伸側リーフバルブＶｅと圧側リーフバルブＶｐがそれぞれシム６５，６１の外周に摺動自在に嵌合されて、ピストン２に対して離間できるようになっているが、内周側が保持軸８ａに固定される構造を採用してもよい。また、電磁圧力制御弁６は、伸側背圧室Ｃｅと圧側背圧室Ｃｐの圧力を調節できればよいので、前述した具体的構造に限定されるものではない。 In the shock absorber D of this example, the extension side leaf valve Ve and the pressure side leaf valve Vp are slidably fitted to the outer circumferences of the shims 65 and 61, respectively, so that they can be separated from the piston 2. However, a structure in which the inner peripheral side is fixed to the holding shaft 8a may be employed. Further, the electromagnetic pressure control valve 6 is not limited to the above-described specific structure because it only needs to be able to adjust the pressure in the extension side back pressure chamber Ce and the pressure side back pressure chamber Cp.
　以上、本発明の好ましい実施の形態を詳細に説明したが、特許請求の範囲から逸脱しない限り、改造、変形、および変更が可能である。 The preferred embodiments of the present invention have been described in detail above, but modifications, changes, and changes can be made without departing from the scope of the claims.
　本願は、２０１７年２月２４日に日本国特許庁に出願された特願２０１７－０３２８２４に基づく優先権を主張し、この出願の全ての内容は参照により本明細書に組み込まれる。 This application claims priority based on Japanese Patent Application No. 2017-032824 filed with the Japan Patent Office on February 24, 2017, the entire contents of which are incorporated herein by reference.

Claims (3)

  1. 　緩衝器であって、
    　シリンダと、
    　シリンダ内に摺動自在に挿入されて前記シリンダ内を伸側室と圧側室とに区画する環状のピストンと、
    　前記ピストンに設けられて前記伸側室と前記圧側室とを連通する伸側通路と圧側通路と、
    　前記ピストンに重ねられて前記伸側通路を開閉する環状の伸側リーフバルブと、
    　前記ピストンに重ねられて前記圧側通路を開閉する環状の圧側リーフバルブと、
    　前記伸側リーフバルブの反ピストン側に配置される環状の伸側チャンバ部材と、
    　前記圧側リーフバルブの反ピストン側に配置される環状の圧側チャンバ部材と、
    　前記伸側リーフバルブの反ピストン側に配置されて前記伸側チャンバ部材に軸方向移動自在に装着され、前記伸側チャンバ部材とともに伸側背圧室を形成するとともに前記伸側背圧室の圧力で前記伸側リーフバルブへ向けて附勢される伸側スプールと、
    　前記圧側リーフバルブの反ピストン側に配置されて前記圧側チャンバ部材に軸方向移動自在に装着され、前記圧側チャンバ部材とともに圧側背圧室を形成するとともに前記圧側背圧室の圧力で前記圧側リーフバルブへ向けて附勢される圧側スプールと、
    　前記ピストン、前記伸側リーフバルブ、前記圧側リーフバルブ、前記伸側チャンバ部材および前記圧側チャンバ部材が外周に装着される保持軸を有するピストンホルダと、
    　液体の流れに抵抗を与える圧側抵抗要素を介して前記伸側背圧室に連通されるとともに通過する液体の流れに抵抗を与える伸側抵抗要素を介して前記圧側背圧室に連通される連通路と、
    　前記連通路を上流として前記連通路に連通される調節通路と、
    　前記調節通路に設けられて上流側の圧力を制御する電磁圧力制御弁と、
    　前記伸側室から前記圧側背圧室へ向かう液体の流れのみを許容する伸側圧力導入通路と、
    　前記圧側室から前記伸側背圧室へ向かう液体の流れのみを許容する圧側圧力導入通路と、
    　前記調節通路の下流を前記圧側室へ連通するとともに前記調節通路から前記圧側室へ向かう液体の流れのみを許容する伸側排出通路と、
    　前記調節通路の下流を前記伸側室へ連通するとともに前記調節通路から前記伸側室へ向かう液体の流れのみを許容する圧側排出通路とを備え、
    　前記連通路は、前記保持軸の外周に形成されている
    　緩衝器。     A shock absorber,
    A cylinder,
    An annular piston that is slidably inserted into the cylinder and divides the cylinder into an extension side chamber and a pressure side chamber;
    An extension side passage and a pressure side passage which are provided in the piston and communicate with the extension side chamber and the pressure side chamber;
    An annular extension leaf valve that is overlapped with the piston and opens and closes the extension passage;
    An annular pressure-side leaf valve that overlaps the piston and opens and closes the pressure-side passage;
    An annular extension chamber member disposed on the non-piston side of the extension leaf valve;
    An annular pressure side chamber member disposed on the anti-piston side of the pressure side leaf valve;
    The extension side leaf valve is disposed on the opposite side of the piston and is mounted on the extension side chamber member so as to be axially movable, and forms an extension side back pressure chamber together with the extension side chamber member, and the pressure of the extension side back pressure chamber An extension side spool biased toward the extension side leaf valve at
    The pressure-side leaf valve is disposed on the side opposite to the piston of the pressure-side leaf valve and is mounted on the pressure-side chamber member so as to be axially movable, and forms a pressure-side back pressure chamber together with the pressure-side chamber member. A pressure-side spool biased toward
    A piston holder having a holding shaft to which the piston, the extension side leaf valve, the pressure side leaf valve, the extension side chamber member and the pressure side chamber member are mounted on the outer periphery;
    A communication communicated with the extension-side back pressure chamber via a compression-side resistance element that provides resistance to the flow of liquid and communicated with the compression-side back pressure chamber via an extension-side resistance element that provides resistance to the flow of liquid passing therethrough. A passage,
    An adjustment passage communicating with the communication passage with the communication passage upstream;
    An electromagnetic pressure control valve provided in the adjustment passage for controlling the pressure on the upstream side;
    An extension side pressure introduction passage that allows only the flow of liquid from the extension side chamber to the compression side back pressure chamber;
    A pressure side pressure introduction passage that allows only a flow of liquid from the pressure side chamber to the extension side back pressure chamber;
    An extension side discharge passage communicating with the pressure side chamber downstream of the adjustment passage and allowing only a flow of liquid from the adjustment passage toward the pressure side chamber;
    A pressure side discharge passage communicating with the extension side chamber downstream of the adjustment passage and allowing only a flow of liquid from the adjustment passage toward the extension side chamber;
    The communication path is formed on an outer periphery of the holding shaft.
  2. 　請求項１に記載の緩衝器であって、
    　前記伸側抵抗要素は、前記圧側チャンバ部材に設けられて前記連通路に連通され、
    　前記圧側抵抗要素は、前記伸側チャンバ部材に設けられて前記連通路に連通される
    　緩衝器。     The shock absorber according to claim 1,
    The extension side resistance element is provided in the compression side chamber member and communicated with the communication path.
    The pressure side resistance element is provided in the extension side chamber member and communicates with the communication path.
  3. 　請求項１に記載の緩衝器であって、
    　前記ピストンホルダの前記保持軸は、前記圧側室に連通される縦孔を有して、前記縦孔で前記伸側排出通路が形成されており、
    　前記縦孔内に前記調節通路から前記圧側室への液体の流れのみを許容する逆止弁の弁座として機能するパイプが設けられる
    　緩衝器。     The shock absorber according to claim 1,
    The holding shaft of the piston holder has a vertical hole communicating with the pressure side chamber, and the extension side discharge passage is formed by the vertical hole,
    A pipe that functions as a valve seat of a check valve that allows only the flow of liquid from the adjustment passage to the pressure side chamber is provided in the vertical hole.
PCT/JP2018/005179 2017-02-24 2018-02-15 Shock absorber WO2018155293A1 (en)

Applications Claiming Priority (2)

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JP2017032824A JP2018136013A (en) 2017-02-24 2017-02-24 Buffer
JP2017-032824 2017-02-24

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022070642A1 (en) * 2020-09-29 2022-04-07 Ｋｙｂ株式会社 Damping valve and shock absorber

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7165032B2 (en) * 2018-11-26 2022-11-02 Ｋｙｂ株式会社 damping valve

Citations (4)

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Publication number Priority date Publication date Assignee Title
JP2005351419A (en) * 2004-06-11 2005-12-22 Kayaba Ind Co Ltd Hydraulic shock absorber
JP2008215433A (en) * 2007-03-01 2008-09-18 Kayaba Ind Co Ltd Valve structure of shock absorber
JP2014031853A (en) * 2012-08-06 2014-02-20 Kayaba Ind Co Ltd Shock absorber
JP2015072047A (en) * 2013-10-03 2015-04-16 カヤバ工業株式会社 Hydraulic shock absorber

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005351419A (en) * 2004-06-11 2005-12-22 Kayaba Ind Co Ltd Hydraulic shock absorber
JP2008215433A (en) * 2007-03-01 2008-09-18 Kayaba Ind Co Ltd Valve structure of shock absorber
JP2014031853A (en) * 2012-08-06 2014-02-20 Kayaba Ind Co Ltd Shock absorber
JP2015072047A (en) * 2013-10-03 2015-04-16 カヤバ工業株式会社 Hydraulic shock absorber

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022070642A1 (en) * 2020-09-29 2022-04-07 Ｋｙｂ株式会社 Damping valve and shock absorber
JP7485579B2 (en) 2020-09-29 2024-05-16 カヤバ株式会社 Damping valves and shock absorbers

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